Multi-speed transmission

ABSTRACT

The present disclosure provides a multiple speed transmission having an input member, an output member, a plurality of planetary gearsets, a plurality of interconnecting members and a plurality of torque-transmitting mechanisms. The plurality of planetary gear sets includes first, second and ring gears. The input member is continuously interconnected with at least one member of one of the plurality of planetary gear sets, and the output member is continuously interconnected with another member of one of the plurality of planetary gear sets. At least eight forward speeds and one reverse speed are achieved by the selective engagement of the five torque-transmitting mechanisms.

RELATED DISCLOSURES

This application is a divisional application of U.S. patent applicationSer. No. 15/498,770, filed Apr. 27, 2017, which is a divisionalapplication of U.S. patent application Ser. No. 14/695,143, filed Apr.24, 2015, now U.S. Pat. No. 9,689,467, both of which are herebyincorporated by reference in their entirety.

FIELD OF THE DISCLOSURE

The present disclosure relates to a multiple speed transmission, and inparticular to a multiple speed transmission capable of achieving eightor more speeds.

BACKGROUND

Multiple speed transmissions use a number of friction clutches orbrakes, planetary gearsets, shafts, and other elements to achieve aplurality of gear or speed ratios. The architecture, i.e., packaging orlayout of the aforementioned elements, is determined based on cost,size, packaging constraints, and desired ratios. There is a need for newarchitectural designs of multiple speed transmissions for achievingdifferent ratios with improved performance, cost, efficiency,responsiveness, and packaging.

SUMMARY

In a first embodiment of the present disclosure, a multiple speedtransmission includes an input member; an output member; first, second,third and fourth planetary gearsets each having first, second and thirdmembers; a plurality of interconnecting members each connected betweenat least one of the first, second, third, and fourth planetary gearsetsand at least another of the first, second, third, and fourth planetarygearsets; a first torque-transmitting mechanism selectively engageableto interconnect the first member of the first planetary gearset and thefirst member of the second planetary gearset with a stationary member; asecond torque-transmitting mechanism selectively engageable tointerconnect the third member of the first planetary gearset with thestationary member; a third torque-transmitting mechanism selectivelyengageable to interconnect the second member of the second planetarygearset with the first member of the fourth planetary gearset and thefirst member of the third planetary gearset; a fourthtorque-transmitting mechanism selectively engageable to interconnect thethird member of the second planetary gearset and the third member of thethird planetary gearset with the second member of the third planetarygearset; and a fifth torque-transmitting mechanism selectivelyengageable to interconnect the second member of the first planetarygearset with the second member of the third planetary gearset; whereinthe torque transmitting mechanisms are selectively engageable incombinations of at least three to establish at least eight forward speedratios and at least one reverse speed ratio between the input member andthe output member.

In a second embodiment, a multiple speed transmission includes an inputmember; an output member; first, second, third and fourth planetarygearsets each having first, second and third members; a plurality ofinterconnecting members each connected between at least one of thefirst, second, third, and fourth planetary gearsets and at least anotherof the first, second, third, and fourth planetary gearsets; a firsttorque-transmitting mechanism selectively engageable to interconnect thefirst member of the first planetary gearset and the first member of thesecond planetary gearset with a stationary member; a secondtorque-transmitting mechanism selectively engageable to interconnect thethird member of the first planetary gearset with the stationary member;a third torque-transmitting mechanism selectively engageable tointerconnect the second member of the second planetary gearset with thefirst member of the fourth planetary gearset and the first member of thethird planetary gearset; a fourth torque-transmitting mechanismselectively engageable to interconnect the second member of the thirdplanetary gearset with the first member of the third planetary gearsetand the first member of the fourth planetary gearset; and a fifthtorque-transmitting mechanism selectively engageable to interconnect thesecond member of the first planetary gearset and the third member of thefourth planetary gearset with the second member of the third planetarygearset; wherein the torque transmitting mechanisms are selectivelyengageable in combinations of at least three to establish at least eightforward speed ratios and at least one reverse speed ratio between theinput member and the output member.

In a third embodiment of the present disclosure, a multiple speedtransmission includes an input member; an output member; first, second,third and fourth planetary gearsets each having first, second and thirdmembers; a plurality of interconnecting members each connected betweenat least one of the first, second, third, and fourth planetary gearsetsand at least another of the first, second, third, and fourth planetarygearsets; a first torque-transmitting mechanism selectively engageableto interconnect the first member of the first planetary gearset and thefirst member of the second planetary gearset with a stationary member; asecond torque-transmitting mechanism selectively engageable tointerconnect the second member of the first planetary gearset with thestationary member; a third torque-transmitting mechanism selectivelyengageable to interconnect the second member of the second planetarygearset with the first member of the third planetary gearset and thefirst member of the fourth planetary gearset; a fourthtorque-transmitting mechanism selectively engageable to interconnect thethird member of the second planetary gearset and the third member of thethird planetary gearset with the first member of the third planetarygearset and the first member of the fourth planetary gearset; and afifth torque-transmitting mechanism selectively engageable tointerconnect the third member of the first planetary gearset and thethird member of the fourth planetary gearset with the second member ofthe third planetary gearset; wherein the torque transmitting mechanismsare selectively engageable in combinations of at least three toestablish at least eight forward speed ratios and at least one reversespeed ratio between the input member and the output member.

In a fourth embodiment, a multiple speed transmission includes an inputmember; an output member; first, second, third and fourth planetarygearsets each having first, second and third members; a plurality ofinterconnecting members each connected between at least one of thefirst, second, third, and fourth planetary gearsets and at least anotherof the first, second, third, and fourth planetary gearsets; a firsttorque-transmitting mechanism selectively engageable to interconnect thefirst member of the first planetary gearset and the first member of thesecond planetary gearset with a stationary member; a secondtorque-transmitting mechanism selectively engageable to interconnect thesecond member of the first planetary gearset with the stationary member;a third torque-transmitting mechanism selectively engageable tointerconnect the second member of the second planetary gearset with thefirst member of the third planetary gearset and the first member of thefourth planetary gearset; a fourth torque-transmitting mechanismselectively engageable to interconnect the third member of the secondplanetary gearset and the third member of the third planetary gearsetwith the second member of the third planetary gearset; and a fifthtorque-transmitting mechanism selectively engageable to interconnect thethird member of the first planetary gearset and the third member of thefourth planetary gearset with the second member of the third planetarygearset; wherein the torque transmitting mechanisms are selectivelyengageable in combinations of at least three to establish at least eightforward speed ratios and at least one reverse speed ratio between theinput member and the output member.

In a fifth embodiment, a multiple speed transmission includes an inputmember; an output member; first, second, third and fourth planetarygearsets each having first, second and third members; a plurality ofinterconnecting members each connected between at least one of thefirst, second, third, and fourth planetary gearsets and at least anotherof the first, second, third, and fourth planetary gearsets; a firsttorque-transmitting mechanism selectively engageable to interconnect thefirst member of the first planetary gearset and the first member of thesecond planetary gearset with a stationary member; a secondtorque-transmitting mechanism selectively engageable to interconnect thesecond member of the first planetary gearset with the stationary member;a third torque-transmitting mechanism selectively engageable tointerconnect the second member of the second planetary gearset with thefirst member of the third planetary gearset and the first member of thefourth planetary gearset; a fourth torque-transmitting mechanismselectively engageable to interconnect the third member of the thirdplanetary gearset with the first member of the third planetary gearsetand the first member of the fourth planetary gearset; and a fifthtorque-transmitting mechanism selectively engageable to interconnect thethird member of the first planetary gearset and the third member of thefourth planetary gearset with the second member of the third planetarygearset; wherein the torque transmitting mechanisms are selectivelyengageable in combinations of at least three to establish at least eightforward speed ratios and at least one reverse speed ratio between theinput member and the output member.

In a sixth embodiment, a multiple speed transmission includes an inputmember; an output member; first, second, third and fourth planetarygearsets each having first, second and third members; a plurality ofinterconnecting members each connected between at least one of thefirst, second, third, and fourth planetary gearsets and at least anotherof the first, second, third, and fourth planetary gearsets; a firsttorque-transmitting mechanism selectively engageable to interconnect thefirst member of the first planetary gearset and the first member of thesecond planetary gearset with a stationary member; a secondtorque-transmitting mechanism selectively engageable to interconnect thethird member of the first planetary gearset with the stationary member;a third torque-transmitting mechanism selectively engageable tointerconnect the third member of the second planetary gearset with thefirst member of the third planetary gearset and the first member of thefourth planetary gearset; a fourth torque-transmitting mechanismselectively engageable to interconnect the second member of the secondplanetary gearset and the third member of the third planetary gearsetwith the first member of the third planetary gearset and the firstmember of the fourth planetary gearset; and a fifth torque-transmittingmechanism selectively engageable to interconnect the second member ofthe first planetary gearset and the third member of the fourth planetarygearset with the second member of the third planetary gearset; whereinthe torque transmitting mechanisms are selectively engageable incombinations of at least three to establish at least eight forward speedratios and at least one reverse speed ratio between the input member andthe output member.

In a seventh embodiment, a multiple speed transmission includes an inputmember; an output member; first, second, third and fourth planetarygearsets each having first, second and third members; a plurality ofinterconnecting members each connected between at least one of thefirst, second, third, and fourth planetary gearsets and at least anotherof the first, second, third, and fourth planetary gearsets; a firsttorque-transmitting mechanism selectively engageable to interconnect thefirst member of the first planetary gearset and the first member of thesecond planetary gearset with a stationary member; a secondtorque-transmitting mechanism selectively engageable to interconnect thethird member of the first planetary gearset with the stationary member;a third torque-transmitting mechanism selectively engageable tointerconnect the third member of the second planetary gearset with thefirst member of the third planetary gearset and the first member of thefourth planetary gearset; a fourth torque-transmitting mechanismselectively engageable to interconnect the second member of the secondplanetary gearset and the third member of the third planetary gearsetwith the second member of the third planetary gearset; and a fifthtorque-transmitting mechanism selectively engageable to interconnect thesecond member of the first planetary gearset and the third member of thefourth planetary gearset with the second member of the third planetarygearset; wherein the torque transmitting mechanisms are selectivelyengageable in combinations of at least three to establish at least eightforward speed ratios and at least one reverse speed ratio between theinput member and the output member.

In an eighth embodiment, a multiple speed transmission includes an inputmember; an output member; first, second, third and fourth planetarygearsets each having first, second and third members; a plurality ofinterconnecting members each connected between at least one of thefirst, second, third, and fourth planetary gearsets and at least anotherof the first, second, third, and fourth planetary gearsets; a firsttorque-transmitting mechanism selectively engageable to interconnect thefirst member of the first planetary gearset and the first member of thesecond planetary gearset with a stationary member; a secondtorque-transmitting mechanism selectively engageable to interconnect thethird member of the first planetary gearset with the stationary member;a third torque-transmitting mechanism selectively engageable tointerconnect the third member of the second planetary gearset with thefirst member of the third planetary gearset and the first member of thefourth planetary gearset; a fourth torque-transmitting mechanismselectively engageable to interconnect the second member of the thirdplanetary gearset with the first member of the third planetary gearsetand the first member of the fourth planetary gearset; and a fifthtorque-transmitting mechanism selectively engageable to interconnect thesecond member of the first planetary gearset and the third member of thefourth planetary gearset with the second member of the third planetarygearset; wherein the torque transmitting mechanisms are selectivelyengageable in combinations of at least three to establish at least eightforward speed ratios and at least one reverse speed ratio between theinput member and the output member.

In a ninth embodiment, a multiple speed transmission includes an inputmember; an output member; first, second, third and fourth planetarygearsets each having first, second and third members; a plurality ofinterconnecting members each connected between at least one of thefirst, second, third, and fourth planetary gearsets and at least anotherof the first, second, third, and fourth planetary gearsets; a firsttorque-transmitting mechanism selectively engageable to interconnect thefirst member of the first planetary gearset and the first member of thesecond planetary gearset with a stationary member; a secondtorque-transmitting mechanism selectively engageable to interconnect thethird member of the first planetary gearset with the stationary member;a third torque-transmitting mechanism selectively engageable tointerconnect the second member of the second planetary gearset with thefirst member of the third planetary gearset and the first member of thefourth planetary gearset; a fourth torque-transmitting mechanismselectively engageable to interconnect the second member of the thirdplanetary gearset with the third member of the third planetary gearset;and a fifth torque-transmitting mechanism selectively engageable tointerconnect the second member of the first planetary gearset and thethird member of the fourth planetary gearset with the third member ofthe third planetary gearset; wherein the torque transmitting mechanismsare selectively engageable in combinations of at least three toestablish at least eight forward speed ratios and at least one reversespeed ratio between the input member and the output member.

In a tenth embodiment of the present disclosure, a multiple speedtransmission includes an input member; an output member; first, second,third and fourth planetary gearsets each having first, second and thirdmembers; a plurality of interconnecting members each connected betweenat least one of the first, second, third, and fourth planetary gearsetsand at least another of the first, second, third, and fourth planetarygearsets; a first torque-transmitting mechanism selectively engageableto interconnect the first member of the first planetary gearset and thefirst member of the second planetary gearset with a stationary member; asecond torque-transmitting mechanism selectively engageable tointerconnect the third member of the first planetary gearset with thestationary member; a third torque-transmitting mechanism selectivelyengageable to interconnect the second member of the second planetarygearset with the first member of the third planetary gearset and thefirst member of the fourth planetary gearset; a fourthtorque-transmitting mechanism selectively engageable to interconnect thethird member of the third planetary gearset with the first member of thethird planetary gearset and the first member of the fourth planetarygearset; and a fifth torque-transmitting mechanism selectivelyengageable to interconnect the second member of the first planetarygearset and the third member of the fourth planetary gearset with thethird member of the third planetary gearset; wherein the torquetransmitting mechanisms are selectively engageable in combinations of atleast three to establish at least eight forward speed ratios and atleast one reverse speed ratio between the input member and the outputmember.

In one or more examples of the embodiments described herein, whenshifting from one forward speed ratio of a multiple speed transmissioninto one of a successive higher and a successive lower forward speedratio causes a single one of the first, the second, the third, thefourth, and the fifth torque transmitting mechanisms to disengage and asingle one of the first, the second, the third, the fourth, and thefifth torque transmitting mechanisms to engage. In another example, thefirst member of each planetary gearset is a sun gear, the second memberof each planetary gearset is a carrier member, and the third member ofeach planetary gearset is a ring gear.

BRIEF DESCRIPTION OF THE DRAWINGS

The above-mentioned aspects of the present disclosure and the manner ofobtaining them will become more apparent and the disclosure itself willbe better understood by reference to the following description of theembodiments of the disclosure, taken in conjunction with theaccompanying drawings, wherein:

FIG. 1 is an exemplary block diagram and schematic view of oneillustrative embodiment of a powered vehicular system;

FIG. 2 is a diagrammatic view of a first embodiment of a multiple speedtransmission;

FIG. 3 is a diagrammatic view of a second embodiment of a multiple speedtransmission;

FIG. 4 is a diagrammatic view of a third embodiment of a multiple speedtransmission;

FIG. 5 is a diagrammatic view of a fourth embodiment of a multiple speedtransmission;

FIG. 6 is a diagrammatic view of a fifth embodiment of a multiple speedtransmission;

FIG. 7 is a diagrammatic view of a sixth embodiment of a multiple speedtransmission;

FIG. 8 is a diagrammatic view of a seventh embodiment of a multiplespeed transmission;

FIG. 9 is a diagrammatic view of an eighth embodiment of a multiplespeed transmission;

FIG. 10 is a diagrammatic view of a ninth embodiment of a multiple speedtransmission;

FIG. 11 is a diagrammatic view of a tenth embodiment of a multiple speedtransmission; and

FIG. 12 is a truth table presenting an example of a state of engagementof various torque transmitting mechanisms in each of the availableforward and reverse speeds or gear ratios of the transmissionsillustrated in FIGS. 2-11.

Corresponding reference numerals are used to indicate correspondingparts throughout the several views.

DETAILED DESCRIPTION

The embodiments of the present disclosure described below are notintended to be exhaustive or to limit the disclosure to the preciseforms disclosed in the following detailed description. Rather, theembodiments are chosen and described so that others skilled in the artmay appreciate and understand the principles and practices of thepresent disclosure.

Referring now to FIG. 1, a block diagram and schematic view of oneillustrative embodiment of a vehicular system 100 having a drive unit102 and transmission 118 is shown. In the illustrated embodiment, thedrive unit 102 may include an internal combustion engine, diesel engine,electric motor, or other power-generating device. The drive unit 102 isconfigured to rotatably drive an output shaft 104 that is coupled to aninput or pump shaft 106 of a conventional torque converter 108. Theinput or pump shaft 106 is coupled to an impeller or pump 110 that isrotatably driven by the output shaft 104 of the drive unit 102. Thetorque converter 108 further includes a turbine 112 that is coupled to aturbine shaft 114, and the turbine shaft 114 is coupled to, or integralwith, a rotatable input shaft 124 of the transmission 118. Thetransmission 118 can also include an internal pump 120 for buildingpressure within different flow circuits (e.g., main circuit, lubecircuit, etc.) of the transmission 118. The pump 120 can be driven by ashaft 116 that is coupled to the output shaft 104 of the drive unit 102.In this arrangement, the drive unit 102 can deliver torque to the shaft116 for driving the pump 120 and building pressure within the differentcircuits of the transmission 118.

The transmission 118 can include a planetary gear system 122 having anumber of automatically selected gears. An output shaft 126 of thetransmission 118 is coupled to or integral with, and rotatably drives, apropeller shaft 128 that is coupled to a conventional universal joint130. The universal joint 130 is coupled to, and rotatably drives, anaxle 132 having wheels 134A and 134B mounted thereto at each end. Theoutput shaft 126 of the transmission 118 drives the wheels 134A and 134Bin a conventional manner via the propeller shaft 128, universal joint130 and axle 132.

A conventional lockup clutch 136 is connected between the pump 110 andthe turbine 112 of the torque converter 108. The operation of the torqueconverter 108 is conventional in that the torque converter 108 isoperable in a so-called “torque converter” mode during certain operatingconditions such as vehicle launch, low speed and certain gear shiftingconditions. In the torque converter mode, the lockup clutch 136 isdisengaged and the pump 110 rotates at the rotational speed of the driveunit output shaft 104 while the turbine 112 is rotatably actuated by thepump 110 through a fluid (not shown) interposed between the pump 110 andthe turbine 112. In this operational mode, torque multiplication occursthrough the fluid coupling such that the turbine shaft 114 is exposed todrive more torque than is being supplied by the drive unit 102, as isknown in the art. The torque converter 108 is alternatively operable ina so-called “lockup” mode during other operating conditions, such aswhen certain gears of the planetary gear system 122 of the transmission118 are engaged. In the lockup mode, the lockup clutch 136 is engagedand the pump 110 is thereby secured directly to the turbine 112 so thatthe drive unit output shaft 104 is directly coupled to the input shaft124 of the transmission 118, as is also known in the art.

The transmission 118 further includes an electro-hydraulic system 138that is fluidly coupled to the planetary gear system 122 via a number,J, of fluid paths, 140 ₁-140 _(J), where J may be any positive integer.The electro-hydraulic system 138 is responsive to control signals toselectively cause fluid to flow through one or more of the fluid paths,140 ₁-140 _(J), to thereby control operation, i.e., engagement anddisengagement, of a plurality of corresponding friction devices in theplanetary gear system 122. The plurality of friction devices mayinclude, but are not limited to, one or more conventional brake devices,one or more torque transmitting devices, and the like. Generally, theoperation, i.e., engagement and disengagement, of the plurality offriction devices is controlled by selectively controlling the frictionapplied by each of the plurality of friction devices, such as bycontrolling fluid pressure to each of the friction devices. In oneexample embodiment, which is not intended to be limiting in any way, theplurality of friction devices include a plurality of brake and torquetransmitting devices in the form of conventional clutches that may eachbe controllably engaged and disengaged via fluid pressure supplied bythe electro-hydraulic system 138. In any case, changing or shiftingbetween the various gears of the transmission 118 is accomplished in aconventional manner by selectively controlling the plurality of frictiondevices via control of fluid pressure within the number of fluid paths140 ₁-140 _(J).

The system 100 further includes a transmission control circuit 142 thatcan include a memory unit 144. The transmission control circuit 142 isillustratively microprocessor-based, and the memory unit 144 generallyincludes instructions stored therein that are executable by a processorof the transmission control circuit 142 to control operation of thetorque converter 108 and operation of the transmission 118, i.e.,shifting between the various gears of the planetary gear system 122. Itwill be understood, however, that this disclosure contemplates otherembodiments in which the transmission control circuit 142 is notmicroprocessor-based, but is configured to control operation of thetorque converter 108 and/or transmission 118 based on one or more setsof hardwired instructions and/or software instructions stored in thememory unit 144.

In the system 100 illustrated in FIG. 1, the torque converter 108 andthe transmission 118 include a number of sensors configured to producesensor signals that are indicative of one or more operating states ofthe torque converter 108 and transmission 118, respectively. Forexample, the torque converter 108 illustratively includes a conventionalspeed sensor 146 that is positioned and configured to produce a speedsignal corresponding to the rotational speed of the pump shaft 106,which is the same rotational speed of the output shaft 104 of the driveunit 102. The speed sensor 146 is electrically connected to a pump speedinput, PS, of the transmission control circuit 142 via a signal path152, and the transmission control circuit 142 is operable to process thespeed signal produced by the speed sensor 146 in a conventional mannerto determine the rotational speed of the pump shaft 106/drive unitoutput shaft 104.

The transmission 118 illustratively includes another conventional speedsensor 148 that is positioned and configured to produce a speed signalcorresponding to the rotational speed of the transmission input shaft124, which is the same rotational speed as the turbine shaft 114. Theinput shaft 124 of the transmission 118 is directly coupled to, orintegral with, the turbine shaft 114, and the speed sensor 148 mayalternatively be positioned and configured to produce a speed signalcorresponding to the rotational speed of the turbine shaft 114. In anycase, the speed sensor 148 is electrically connected to a transmissioninput shaft speed input, TIS, of the transmission control circuit 142via a signal path 154, and the transmission control circuit 142 isoperable to process the speed signal produced by the speed sensor 148 ina conventional manner to determine the rotational speed of the turbineshaft 114/transmission input shaft 124.

The transmission 118 further includes yet another speed sensor 150 thatis positioned and configured to produce a speed signal corresponding tothe rotational speed of the output shaft 126 of the transmission 118.The speed sensor 150 may be conventional, and is electrically connectedto a transmission output shaft speed input, TOS, of the transmissioncontrol circuit 142 via a signal path 156. The transmission controlcircuit 142 is configured to process the speed signal produced by thespeed sensor 150 in a conventional manner to determine the rotationalspeed of the transmission output shaft 126.

In the illustrated embodiment, the transmission 118 further includes oneor more actuators configured to control various operations within thetransmission 118. For example, the electro-hydraulic system 138described herein illustratively includes a number of actuators, e.g.,conventional solenoids or other conventional actuators, that areelectrically connected to a number, J, of control outputs, CP₁-CP_(J),of the transmission control circuit 142 via a corresponding number ofsignal paths 72 ₁-72 _(J), where J may be any positive integer asdescribed above. The actuators within the electro-hydraulic system 138are each responsive to a corresponding one of the control signals,CP₁-CP_(J), produced by the transmission control circuit 142 on one ofthe corresponding signal paths 72 ₁-72 _(J) to control the frictionapplied by each of the plurality of friction devices by controlling thepressure of fluid within one or more corresponding fluid passageway 140₁-140 _(J), and thus control the operation, i.e., engaging anddisengaging, of one or more corresponding friction devices, based oninformation provided by the various speed sensors 146, 148, and/or 150.

The friction devices of the planetary gear system 122 are illustrativelycontrolled by hydraulic fluid which is distributed by theelectro-hydraulic system in a conventional manner. For example, theelectro-hydraulic system 138 illustratively includes a conventionalhydraulic positive displacement pump (not shown) which distributes fluidto the one or more friction devices via control of the one or moreactuators within the electro-hydraulic system 138. In this embodiment,the control signals, CP₁-CP_(J), are illustratively analog frictiondevice pressure commands to which the one or more actuators areresponsive to control the hydraulic pressure to the one or morefrictions devices. It will be understood, however, that the frictionapplied by each of the plurality of friction devices may alternativelybe controlled in accordance with other conventional friction devicecontrol structures and techniques, and such other conventional frictiondevice control structures and techniques are contemplated by thisdisclosure. In any case, however, the analog operation of each of thefriction devices is controlled by the control circuit 142 in accordancewith instructions stored in the memory unit 144.

In the illustrated embodiment, the system 100 further includes a driveunit control circuit 160 having an input/output port (I/O) that iselectrically coupled to the drive unit 102 via a number, K, of signalpaths 162, wherein K may be any positive integer. The drive unit controlcircuit 160 may be conventional, and is operable to control and managethe overall operation of the drive unit 102. The drive unit controlcircuit 160 further includes a communication port, COM, which iselectrically connected to a similar communication port, COM, of thetransmission control circuit 142 via a number, L, of signal paths 164,wherein L may be any positive integer. The one or more signal paths 164are typically referred to collectively as a data link. Generally, thedrive unit control circuit 160 and the transmission control circuit 142are operable to share information via the one or more signal paths 164in a conventional manner. In one embodiment, for example, the drive unitcontrol circuit 160 and transmission control circuit 142 are operable toshare information via the one or more signal paths 164 in the form ofone or more messages in accordance with a society of automotiveengineers (SAE) J-1939 communications protocol, although this disclosurecontemplates other embodiments in which the drive unit control circuit160 and the transmission control circuit 142 are operable to shareinformation via the one or more signal paths 164 in accordance with oneor more other conventional communication protocols (e.g., from aconventional databus such as J1587 data bus, J1939 data bus, IESCAN databus, GMLAN, Mercedes PT-CAN).

Referring to FIG. 2, a schematic representation or stick diagramillustrates one embodiment of a multi-speed transmission 200 accordingto the present disclosure. The transmission 200 includes an input shaft202 and an output shaft 204. The input shaft 202 and output shaft 204can be disposed along the same axis or centerline of the transmission200. In another aspect, the different shafts can be disposed alongdifferent axes or centerlines. In a further aspect, the different shaftscan be disposed parallel to one another, but along different axes orcenterlines. Other aspect can be appreciated by one skilled in the art.

The transmission 200 can also include a plurality of planetary gearsets.In the illustrated embodiment of FIG. 2, the transmission 200 includes afirst planetary gearset 206, a second planetary gearset 208, a thirdplanetary gearset 210, and a fourth planetary gearset 212. Eachplanetary gearset can be referred to as a simple or compound planetarygearset. For example, in some aspects, one or more of the plurality ofplanetary gearsets can be formed as an idler planetary gearset. In FIG.2, however, each of the planetary gearsets is formed as a simpleplanetary gearset.

One or more of the plurality of planetary gearsets can be arranged indifferent locations within the transmission 200, but for sake ofsimplicity and in this particular example only, the planetary gearsetsare aligned in an axial direction consecutively in sequence (i.e.,first, second, third, and fourth between the input and output shafts).

The transmission 200 may also include a plurality of torque-transmittingor gearshifting mechanisms. For example, one or more of these mechanismscan include a clutch or brake. In one aspect, each of the plurality ofmechanisms is disposed within an outer housing of the transmission 200.In another aspect, however, one or more of the mechanisms may bedisposed outside of the housing. Each of the plurality of mechanisms canbe coupled to one or more of the plurality of planetary gearsets, whichwill be described further below.

In the embodiment of FIG. 2, the transmission 200 can include a firsttorque-transmitting mechanism 258 and a second torque-transmittingmechanism 260 that are configured to function as brakes (e.g., thetorque-transmitting mechanism is fixedly coupled to the outer housing ofthe transmission 200). Each brake can be configured as ashiftable-friction-locked disk brake, shiftable friction-locked bandbrake, shiftable form-locking claw or conical brake, or any other typeof known brake. The transmission 200 can include a thirdtorque-transmitting mechanism 262, a fourth torque-transmittingmechanism 264, and a fifth torque-transmitting mechanism 266 that areconfigured to function as clutches. These can be shiftablefriction-locked multi-disk clutches, shiftable form-locking claw orconical clutches, wet clutches, or any other known form of a clutch.With these five torque-transmitting mechanisms, selective shifting of atleast eight forward gears and at least one reverse gear is possible.

The transmission 200 of FIG. 2 may also include up to eight differentshafts, which is inclusive of the input shaft 202 and output shaft 204.Each of these shafts, designated as a first shaft 222, a second shaft224, a third shaft 226, a fourth shaft 236, a fifth shaft 246, and asixth shaft 248, are configured to be connected to one or more of theplurality of planetary gearsets or plurality of torque-transmittingmechanism between the input shaft 202 and output shaft 204.

In FIG. 2, the first planetary gearset 206 can include a first sun gear214, a first ring gear 216, and a first carrier member 218 thatrotatably supports a set of pinion gears 220. The second planetarygearset 208 can include a second sun gear 228, a second ring gear 230,and a second carrier member 232 that rotatably supports a set of piniongears 234. The third planetary gearset 210 can include a third sun gear238, a third ring gear 240, and a third carrier member 242 thatrotatably supports a set of pinion gears 244. The fourth planetarygearset 212 can include a fourth sun gear 250, a fourth ring gear 252,and a fourth carrier member 254 that rotatably supports a set of piniongears 256.

The transmission 200 is capable of transferring torque from the inputshaft 202 to the output shaft 204 in at least eight forward gears orratios and at least one reverse gear or ratio. Each of the forwardtorque ratios and the reverse torque ratios can be attained by theselective engagement of one or more of the torque-transmittingmechanisms (i.e., torque-transmitting mechanisms 258, 260, 262, 264, and266). Those skilled in the art will readily understand that a differentspeed ratio is associated with each torque ratio. Thus, at least eightforward speed ratios and at least one reverse speed ratio may beattained by transmission 200.

As for the transmission 200, kinematic coupling of the first planetarygearset 206 is shown in FIG. 2. The first sun gear 214 is coupled to thefirst shaft 222 for common rotation therewith. The first carrier member218 is coupled to the third shaft 226 for common rotation therewith.First ring gear 216 is coupled for common rotation with the second shaft224.

With respect to the second planetary gearset 208, the second sun gear228 is coupled to the first shaft 222 and first sun gear 214 for commonrotation therewith. The second ring gear 230 is coupled to the thirdshaft 236 for common rotation therewith. Second pinion gears 234 areconfigured to intermesh with the second sun gear 228 and second ringgear 230, and the second carrier member 232 is coupled for commonrotation with the input shaft 202.

The third sun gear 238 of the third planetary gearset 210 is coupled tothe sixth shaft 248 for common rotation therewith. The third ring gear240 is coupled to the fourth shaft 236, which is also coupled to thesecond ring gear 230, for common rotation therewith. Third pinion gears244 are configured to intermesh with the third sun gear 238 and thirdring gear 240, respectively. The third carrier member 242 is coupled forcommon rotation with the fifth shaft 246.

The kinematic relationship of the fourth planetary gearset 212 is suchthat the fourth sun gear 250 is coupled to the sixth shaft 248, which isalso coupled to the third sun gear 238 for common rotation therewith.The fourth ring gear 252 is coupled to the third shaft 226 and firstcarrier member 218 for common rotation therewith. The fourth piniongears 256 are configured to intermesh with the fourth sun gear 250 andthe fourth ring gear 252. The fourth carrier member 254 is coupled tothe output shaft 204 for common rotation therewith.

With regards to the kinematic coupling of the five torque-transmittingmechanisms to the previously described shafts, the multiple speedtransmission 200 of FIG. 2 provides that the first torque-transmittingmechanism 258 is arranged within the power flow between the first shaft222 and a housing G of the transmission 200. In this manner, the firsttorque-transmitting mechanism 258 is configured to act as a brake. Thesecond torque-transmitting mechanism 260 is arranged within the powerflow between the second shaft 224 and the housing G of the transmission200. In this manner, the second torque-transmitting mechanism 260 isconfigured to act as a brake. In this embodiment of the transmission 200therefore two of the five torque-transmitting mechanisms are configuredto act as a brake and the other three torque-transmitting mechanisms areconfigured to act as clutches.

The third torque-transmitting mechanism 262, for example, is arrangedwithin the power flow between the input shaft 202 and the sixth shaft248. The fourth torque-transmitting mechanism 264 is arranged within thepower flow between the fourth shaft 236 and the fifth shaft 246.Moreover, the fifth torque-transmitting mechanism 266 is arranged withinthe power flow between the third shaft 226 and the fifth shaft 246.

The kinematic couplings of the embodiment in FIG. 2 can further bedescribed with respect to the selective engagement of thetorque-transmitting mechanisms with respect to one or more components ofthe plurality of planetary gearsets. For example, in the transmission200, the first torque-transmitting mechanism 258 is selectivelyengageable to couple the first sun gear 214, the second sun gear 228,and the first shaft 222 to the housing G of the transmission 200. Thesecond torque-transmitting mechanism 260 is selectively engageable tocouple the first ring gear 216 and the second shaft 224 to the housing Gof the transmission 200. Moreover, the third torque-transmittingmechanism 262 is selectively engageable to couple input shaft 202 andthe second carrier member 232 to the sixth shaft 248, third sun gear 238and fourth sun gear 250. The fourth torque-transmitting mechanism 264 isselectively engageable to couple fourth shaft 236, the second ring gear230, and the third ring gear 240 to the third carrier member 242 and thefifth shaft 246. Lastly, the fifth torque-transmitting mechanism 266 isselectively engageable to couple the third shaft 226, the first carriermember 218, and fourth ring gear 252 to the fifth shaft 246 and thethird carrier member 242.

Referring to FIG. 3, a schematic representation or stick diagramillustrates one embodiment of a multi-speed transmission 300 accordingto the present disclosure. The transmission 300 includes an input shaft302 and an output shaft 304. The input shaft 302 and output shaft 304can be disposed along the same axis or centerline of the transmission300. In another aspect, the different shafts can be disposed alongdifferent axes or centerlines. In a further aspect, the different shaftscan be disposed parallel to one another, but along different axes orcenterlines. Other aspect can be appreciated by one skilled in the art.

The transmission 300 can also include a plurality of planetary gearsets.In the illustrated embodiment of FIG. 3, the transmission 300 includes afirst planetary gearset 306, a second planetary gearset 308, a thirdplanetary gearset 310, and a fourth planetary gearset 312. Eachplanetary gearset can be referred to as a simple or compound planetarygearset. For example, in some aspects, one or more of the plurality ofplanetary gearsets can be formed as an idler planetary gearset. In FIG.3, each planetary gearset is a simple planetary gearset.

One or more of the plurality of planetary gearsets can be arranged indifferent locations within the transmission 300, but for sake ofsimplicity and in this particular example only, the planetary gearsetsare aligned in an axial direction consecutively in sequence (i.e.,first, second, third, and fourth between the input and output shafts).

The transmission 300 may also include a plurality of torque-transmittingor gearshifting mechanisms. For example, one or more of these mechanismscan include a clutch or brake. In one aspect, each of the plurality ofmechanisms is disposed within an outer housing of the transmission 300.In another aspect, however, one or more of the mechanisms may bedisposed outside of the housing. Each of the plurality of mechanisms canbe coupled to one or more of the plurality of planetary gearsets, whichwill be described further below.

In the embodiment of FIG. 3, the transmission 300 can include a firsttorque-transmitting mechanism 358 and a second torque-transmittingmechanism 360 that are configured to function as brakes (e.g., thetorque-transmitting mechanism is fixedly coupled to the outer housing ofthe transmission 300). Each brake can be configured as ashiftable-friction-locked disk brake, shiftable friction-locked bandbrake, shiftable form-locking claw or conical brake, or any other typeof known brake. The transmission 300 can include a thirdtorque-transmitting mechanism 362, a fourth torque-transmittingmechanism 364, and a fifth torque-transmitting mechanism 366 that areconfigured to function as clutches. These can be shiftablefriction-locked multi-disk clutches, shiftable form-locking claw orconical clutches, wet clutches, or any other known form of a clutch.With these five torque-transmitting mechanisms, selective shifting of atleast eight forward gears and at least one reverse gear is possible.

The transmission 300 of FIG. 3 may also include up to eight differentshafts, which is inclusive of the input shaft 302 and output shaft 304.Each of these shafts, designated as a first shaft 322, a second shaft324, a third shaft 326, a fourth shaft 336, a fifth shaft 346, and asixth shaft 348, are configured to be connected to one or more of theplurality of planetary gearsets or plurality of torque-transmittingmechanism between the input shaft 302 and output shaft 304.

In FIG. 3, the first planetary gearset 306 can include a first sun gear314, a first ring gear 316, and a first carrier member 318 thatrotatably supports a set of pinion gears 320. The second planetarygearset 308 can include a second sun gear 328, a second ring gear 330,and a second carrier member 332 that rotatably supports a set of piniongears 334. The third planetary gearset 310 can include a third sun gear338, a third ring gear 340, and a third carrier member 342 thatrotatably supports a set of pinion gears 344. The fourth planetarygearset 312 can include a fourth sun gear 350, a fourth ring gear 352,and a fourth carrier member 354 that rotatably supports a set of piniongears 356.

The transmission 300 is capable of transferring torque from the inputshaft 302 to the output shaft 304 in at least eight forward gears orratios and at least one reverse gear or ratio. Each of the forwardtorque ratios and the reverse torque ratios can be attained by theselective engagement of one or more of the torque-transmittingmechanisms (i.e., torque-transmitting mechanisms 358, 360, 362, 364, and366). Those skilled in the art will readily understand that a differentspeed ratio is associated with each torque ratio. Thus, at least eightforward speed ratios and at least one reverse speed ratio may beattained by transmission 300.

As for the transmission 300, kinematic coupling of the first planetarygearset 306 is shown in FIG. 3. The first sun gear 314 is coupled to thefirst shaft 322 for common rotation therewith. The first carrier member318 is coupled to the third shaft 326 for common rotation therewith.First ring gear 316 is coupled for common rotation with the second shaft324.

With respect to the second planetary gearset 308, the second sun gear328 is coupled to the first shaft 322 and first sun gear 314 for commonrotation therewith. The second ring gear 330 is coupled to the fourthshaft 336 for common rotation therewith. The second carrier member 332is coupled for common rotation with the input shaft 302.

The third sun gear 338 of the third planetary gearset 310 is coupled tothe sixth shaft 348 for common rotation therewith. The third ring gear340 is coupled to the fourth shaft 336 for common rotation therewith.Third pinion gears 344 are configured to intermesh with the third sungear 338 and third ring gear 340, respectively. The third carrier member342 is coupled for common rotation with the fifth shaft 346.

The kinematic relationship of the fourth planetary gearset 312 is suchthat the fourth sun gear 350 is coupled to the sixth shaft 348 forcommon rotation therewith. The fourth ring gear 352 is coupled to thethird shaft 326 for common rotation therewith. The fourth pinion gears356 are configured to intermesh with the fourth sun gear 350 and thefourth ring gear 352. The fourth carrier member 354 is coupled to theoutput shaft 304 for common rotation therewith.

With regards to the kinematic coupling of the five torque-transmittingmechanisms to the previously described shafts, the multiple speedtransmission 300 of FIG. 3 provides that the first torque-transmittingmechanism 358 is arranged within the power flow between the first shaft322 and a housing G of the transmission 300. In this manner, the firsttorque-transmitting mechanism 358 is configured to act as a brake. Thesecond torque-transmitting mechanism 360 is arranged within the powerflow between the second shaft 324 and the housing G of the transmission300. In this manner, the second torque-transmitting mechanism 360 isconfigured to act as a brake. In this embodiment of the transmission 300therefore two of the five torque-transmitting mechanisms are configuredto act as a brake and the other three torque-transmitting mechanisms areconfigured to act as clutches.

The third torque-transmitting mechanism 362, for example, is arrangedwithin the power flow between the input shaft 302 and the sixth shaft348. The fourth torque-transmitting mechanism 364 is arranged within thepower flow between the fifth shaft 346 and the sixth shaft 348.Moreover, the fifth torque-transmitting mechanism 366 is arranged withinthe power flow between the third shaft 326 and the fifth shaft 346.

The kinematic couplings of the embodiment in FIG. 3 can further bedescribed with respect to the selective engagement of thetorque-transmitting mechanisms with respect to one or more components ofthe plurality of planetary gearsets. For example, in the transmission300, the first torque-transmitting mechanism 358 is selectivelyengageable to couple the first sun gear 314, the second sun gear 328,and the first shaft 322 to the housing G of the transmission 300. Thesecond torque-transmitting mechanism 360 is selectively engageable tocouple the first ring gear 316 and the second shaft 324 to the housing Gof the transmission 300. Moreover, the third torque-transmittingmechanism 362 is selectively engageable to couple input shaft 302 andthe second carrier member 332 to the sixth shaft 348, the third sun gear338, and fourth sun gear 350. The fourth torque-transmitting mechanism364 is selectively engageable to couple fifth shaft 346 and the thirdcarrier member 342 to the third sun gear 338, fourth sun gear 350, andthe sixth shaft 348. Lastly, the fifth torque-transmitting mechanism 366is selectively engageable to couple the second carrier member 318, thefourth ring gear 352 and the third shaft 326 to the fifth shaft 346 andthird carrier member 342.

Referring to FIG. 4, a schematic representation or stick diagramillustrates one embodiment of a multi-speed transmission 400 accordingto the present disclosure. The transmission 400 includes an input shaft402 and an output shaft 404. The input shaft 402 and output shaft 404can be disposed along the same axis or centerline of the transmission400. In another aspect, the different shafts can be disposed alongdifferent axes or centerlines. In a further aspect, the different shaftscan be disposed parallel to one another, but along different axes orcenterlines. Other aspect can be appreciated by one skilled in the art.

The transmission 400 can also include a plurality of planetary gearsets.In the illustrated embodiment of FIG. 4, the transmission 400 includes afirst planetary gearset 406, a second planetary gearset 408, a thirdplanetary gearset 410, and a fourth planetary gearset 412. Eachplanetary gearset can be referred to as a simple or compound planetarygearset. For example, in some aspects, one or more of the plurality ofplanetary gearsets can be formed as an idler planetary gearset. In FIG.4, for instance, the first planetary gearset 406 is structurally setforth as an idler planetary gearset. In this example, an idler planetplanetary gearset can include a sun gear, a ring gear, a carrier, andtwo sets of pinion gears. One set of pinion gears can be rotationallycoupled with the sun gear and the other set of pinion gears can berotationally coupled to the ring gear. Both sets of pinion gears arecoupled to one another such that one pinion gear of the first set isrotationally coupled to one pinion gear of the second set. In thismanner, power can be transferred through the sun or ring gear via eachof the sets of pinion gears.

One or more of the plurality of planetary gearsets can be arranged indifferent locations within the transmission 400, but for sake ofsimplicity and in this particular example only, the planetary gearsetsare aligned in an axial direction consecutively in sequence (i.e.,first, second, third, and fourth between the input and output shafts).

The transmission 400 may also include a plurality of torque-transmittingor gearshifting mechanisms. For example, one or more of these mechanismscan include a clutch or brake. In one aspect, each of the plurality ofmechanisms is disposed within an outer housing of the transmission 400.In another aspect, however, one or more of the mechanisms may bedisposed outside of the housing. Each of the plurality of mechanisms canbe coupled to one or more of the plurality of planetary gearsets, whichwill be described further below.

In the embodiment of FIG. 4, the transmission 400 can include a firsttorque-transmitting mechanism 458 and a second torque-transmittingmechanism 460 that are configured to function as brakes (e.g., thetorque-transmitting mechanism is fixedly coupled to the outer housing ofthe transmission 400). Each brake can be configured as ashiftable-friction-locked disk brake, shiftable friction-locked bandbrake, shiftable form-locking claw or conical brake, or any other typeof known brake. The transmission 400 can include a thirdtorque-transmitting mechanism 462, a fourth torque-transmittingmechanism 464, and a fifth torque-transmitting mechanism 466 that areconfigured to function as clutches. These can be shiftablefriction-locked multi-disk clutches, shiftable form-locking claw orconical clutches, wet clutches, or any other known form of a clutch.With these five torque-transmitting mechanisms, selective shifting of atleast eight forward gears and at least one reverse gear is possible.

The transmission 400 of FIG. 4 may also include up to eight differentshafts, which is inclusive of the input shaft 402 and output shaft 404.Each of these shafts, designated as a first shaft 422, a second shaft424, a third shaft 426, a fourth shaft 436, a fifth shaft 446, and asixth shaft 448, are configured to be connected to one or more of theplurality of planetary gearsets or plurality of torque-transmittingmechanism between the input shaft 402 and output shaft 404.

In FIG. 4, the first planetary gearset 406, i.e., the idler planetarygearset, can include a first sun gear 414, a first ring gear 416, and afirst carrier member 418 that rotatably supports two sets of piniongears 420, 468. One set of pinion gears 468 is rotationally coupled tothe sun gear 414 and the other set of pinion gears 420 is rotationallycoupled to the ring gear 416. The pinion gears 420, 468 are alsorotationally coupled to one another, as is the case in each architecturedescribed herein that includes an idler planetary gearset. The secondplanetary gearset 408 can include a second sun gear 428, a second ringgear 430, and a second carrier member 432 that rotatably supports a setof pinion gears 434. The third planetary gearset 410 can include a thirdsun gear 438, a third ring gear 440, and a third carrier member 442 thatrotatably supports a set of pinion gears 444. The fourth planetarygearset 412 can include a fourth sun gear 450, a fourth ring gear 452,and a fourth carrier member 454 that rotatably supports a set of piniongears 456.

The transmission 400 is capable of transferring torque from the inputshaft 402 to the output shaft 404 in at least eight forward gears orratios and at least one reverse gear or ratio. Each of the forwardtorque ratios and the reverse torque ratios can be attained by theselective engagement of one or more of the torque-transmittingmechanisms (i.e., torque-transmitting mechanisms 458, 460, 462, 464, and466). Those skilled in the art will readily understand that a differentspeed ratio is associated with each torque ratio. Thus, at least eightforward speed ratios and at least one reverse speed ratio may beattained by transmission 400.

As for the transmission 400, kinematic coupling of the first planetarygearset 406 is shown in FIG. 4. The first sun gear 414 is coupled to thefirst shaft 422 for common rotation therewith. The first carrier member418 is coupled to the second shaft 424 for common rotation therewith.First ring gear 416 is coupled for common rotation with the third shaft426.

With respect to the second planetary gearset 408, the second sun gear428 is coupled to the first shaft 422 and first sun gear 414 for commonrotation therewith. The second ring gear 430 is coupled to the fourthshaft 436 for common rotation therewith. The second carrier member 432is coupled for common rotation with the input shaft 402.

The third sun gear 438 of the third planetary gearset 410 is coupled tothe sixth shaft 448 for common rotation therewith. The third ring gear440 is coupled to the fourth shaft 436 for common rotation therewith.Third pinion gears 444 are configured to intermesh with the third sungear 438 and third ring gear 440, respectively. The third carrier member442 is coupled for common rotation with the fifth shaft 446.

The kinematic relationship of the fourth planetary gearset 412 is suchthat the fourth sun gear 450 is coupled to the sixth shaft 448 forcommon rotation therewith. The fourth ring gear 452 is coupled to thethird shaft 426 for common rotation therewith. The fourth pinion gears456 are configured to intermesh with the fourth sun gear 450 and thefourth ring gear 452. The fourth carrier member 454 is coupled to theoutput shaft 404 for common rotation therewith.

With regards to the kinematic coupling of the five torque-transmittingmechanisms to the previously described shafts, the multiple speedtransmission 400 of FIG. 4 provides that the first torque-transmittingmechanism 458 is arranged within the power flow between the first shaft422 and a housing G of the transmission 400. In this manner, the firsttorque-transmitting mechanism 458 is configured to act as a brake. Thesecond torque-transmitting mechanism 460 is arranged within the powerflow between the second shaft 424 and the housing G of the transmission400. In this manner, the second torque-transmitting mechanism 460 isconfigured to act as a brake. In this embodiment of the transmission 400therefore two of the five torque-transmitting mechanisms are configuredto act as a brake and the other three torque-transmitting mechanisms areconfigured to act as clutches.

The third torque-transmitting mechanism 462, for example, is arrangedwithin the power flow between the input shaft 402 and the sixth shaft448. The fourth torque-transmitting mechanism 464 is arranged within thepower flow between the fourth shaft 436 and the sixth shaft 448.Moreover, the fifth torque-transmitting mechanism 466 is arranged withinthe power flow between the third shaft 426 and the fifth shaft 446.

The kinematic couplings of the embodiment in FIG. 4 can further bedescribed with respect to the selective engagement of thetorque-transmitting mechanisms with respect to one or more components ofthe plurality of planetary gearsets. For example, in the transmission400, the first torque-transmitting mechanism 458 is selectivelyengageable to couple the first sun gear 414, the second sun gear 428,and the first shaft 422 to the housing G of the transmission 400. Thesecond torque-transmitting mechanism 460 is selectively engageable tocouple the first carrier member 418 and the second shaft 424 to thehousing G of the transmission 400. Moreover, the thirdtorque-transmitting mechanism 462 is selectively engageable to coupleinput shaft 402 and the second carrier member 432 to the sixth shaft448, the third sun gear 438, and fourth sun gear 450. The fourthtorque-transmitting mechanism 464 is selectively engageable to couplefourth shaft 436, the second ring gear 430, and third ring gear 440 tothe third sun gear 438, fourth sun gear 450 and the sixth shaft 448.Lastly, the fifth torque-transmitting mechanism 466 is selectivelyengageable to couple the first ring gear 416, the fourth ring gear 452,and the third shaft 426 to the fifth shaft 446 and the third carriermember 442.

Referring to FIG. 5, a schematic representation or stick diagramillustrates one embodiment of a multi-speed transmission 500 accordingto the present disclosure. The transmission 500 includes an input shaft502 and an output shaft 504. The input shaft 502 and output shaft 504can be disposed along the same axis or centerline of the transmission500. In another aspect, the different shafts can be disposed alongdifferent axes or centerlines. In a further aspect, the different shaftscan be disposed parallel to one another, but along different axes orcenterlines. Other aspect can be appreciated by one skilled in the art.

The transmission 500 can also include a plurality of planetary gearsets.In the illustrated embodiment of FIG. 5, the transmission 500 includes afirst planetary gearset 506, a second planetary gearset 508, a thirdplanetary gearset 510, and a fourth planetary gearset 512. Eachplanetary gearset can be referred to as a simple or compound planetarygearset. For example, in some aspects, one or more of the plurality ofplanetary gearsets can be formed as an idler planetary gearset. In FIG.5, for instance, the first planetary gearset 506 is structurally setforth as an idler planetary gearset. In this example, an idler planetplanetary gearset can include a sun gear, a ring gear, a carrier, andtwo sets of pinion gears. One set of pinion gears can be rotationallycoupled with the sun gear and the other set of pinion gears can berotationally coupled to the ring gear. Both sets of pinion gears arecoupled to one another such that one pinion gear of the first set isrotationally coupled to one pinion gear of the second set. In thismanner, power can be transferred through the sun or ring gear via eachof the sets of pinion gears.

One or more of the plurality of planetary gearsets can be arranged indifferent locations within the transmission 500, but for sake ofsimplicity and in this particular example only, the planetary gearsetsare aligned in an axial direction consecutively in sequence (i.e.,first, second, third, and fourth between the input and output shafts).

The transmission 500 may also include a plurality of torque-transmittingor gearshifting mechanisms. For example, one or more of these mechanismscan include a clutch or brake. In one aspect, each of the plurality ofmechanisms is disposed within an outer housing of the transmission 500.In another aspect, however, one or more of the mechanisms may bedisposed outside of the housing. Each of the plurality of mechanisms canbe coupled to one or more of the plurality of planetary gearsets, whichwill be described further below.

In the embodiment of FIG. 5, the transmission 500 can include a firsttorque-transmitting mechanism 558 and a second torque-transmittingmechanism 560 that are configured to function as brakes (e.g., thetorque-transmitting mechanism is fixedly coupled to the outer housing ofthe transmission 500). Each brake can be configured as ashiftable-friction-locked disk brake, shiftable friction-locked bandbrake, shiftable form-locking claw or conical brake, or any other typeof known brake. The transmission 500 can include a thirdtorque-transmitting mechanism 562, a fourth torque-transmittingmechanism 564, and a fifth torque-transmitting mechanism 566 that areconfigured to function as clutches. These can be shiftablefriction-locked multi-disk clutches, shiftable form-locking claw orconical clutches, wet clutches, or any other known form of a clutch.With these five torque-transmitting mechanisms, selective shifting of atleast eight forward gears and at least one reverse gear is possible.

The transmission 500 of FIG. 5 may also include up to eight differentshafts, which is inclusive of the input shaft 502 and output shaft 504.Each of these shafts, designated as a first shaft 522, a second shaft524, a third shaft 526, a fourth shaft 536, a fifth shaft 546, and asixth shaft 548, are configured to be connected to one or more of theplurality of planetary gearsets or plurality of torque-transmittingmechanism between the input shaft 502 and output shaft 504.

In FIG. 5, the first planetary gearset 506, i.e., the idler planetarygearset, can include a first sun gear 514, a first ring gear 516, and afirst carrier member 518 that rotatably supports two sets of piniongears 520, 568. One set of pinion gears 568 is rotationally coupled tothe sun gear 514 and the other set of pinion gears 520 is rotationallycoupled to the ring gear 516. The second planetary gearset 508 caninclude a second sun gear 528, a second ring gear 530, and a secondcarrier member 532 that rotatably supports a set of pinion gears 534.The third planetary gearset 510 can include a third sun gear 538, athird ring gear 540, and a third carrier member 542 that rotatablysupports a set of pinion gears 544. The fourth planetary gearset 512 caninclude a fourth sun gear 550, a fourth ring gear 552, and a fourthcarrier member 554 that rotatably supports a set of pinion gears 556.

The transmission 500 is capable of transferring torque from the inputshaft 502 to the output shaft 504 in at least eight forward gears orratios and at least one reverse gear or ratio. Each of the forwardtorque ratios and the reverse torque ratios can be attained by theselective engagement of one or more of the torque-transmittingmechanisms (i.e., torque-transmitting mechanisms 558, 560, 562, 564, and566). Those skilled in the art will readily understand that a differentspeed ratio is associated with each torque ratio. Thus, at least eightforward speed ratios and at least one reverse speed ratio may beattained by transmission 500.

As for the transmission 500, kinematic coupling of the first planetarygearset 506 is shown in FIG. 5. The first sun gear 514 is coupled to thefirst shaft 522 for common rotation therewith. The first carrier member518 is coupled to the second shaft 524 for common rotation therewith.First ring gear 516 is coupled for common rotation with the third shaft526.

With respect to the second planetary gearset 508, the second sun gear528 is coupled to the first shaft 522 and first sun gear 514 for commonrotation therewith. The second ring gear 530 is coupled to the fourthshaft 536 for common rotation therewith. The second carrier member 532is coupled for common rotation with the input shaft 502.

The third sun gear 538 of the third planetary gearset 510 is coupled tothe sixth shaft 548 for common rotation therewith. The third ring gear540 is coupled to the fourth shaft 536 for common rotation therewith.Third pinion gears 544 are configured to intermesh with the third sungear 538 and third ring gear 540, respectively. The third carrier member542 is coupled for common rotation with the fifth shaft 546.

The kinematic relationship of the fourth planetary gearset 512 is suchthat the fourth sun gear 550 is coupled to the sixth shaft 548 forcommon rotation therewith. The fourth ring gear 552 is coupled to thethird shaft 526 for common rotation therewith. The fourth pinion gears556 are configured to intermesh with the fourth sun gear 550 and thefourth ring gear 552. The fourth carrier member 554 is coupled to theoutput shaft 504 for common rotation therewith.

With regards to the kinematic coupling of the five torque-transmittingmechanisms to the previously described shafts, the multiple speedtransmission 500 of FIG. 5 provides that the first torque-transmittingmechanism 558 is arranged within the power flow between the first shaft522 and a housing G of the transmission 500. In this manner, the firsttorque-transmitting mechanism 558 is configured to act as a brake. Thesecond torque-transmitting mechanism 560 is arranged within the powerflow between the second shaft 524 and the housing G of the transmission500. In this manner, the second torque-transmitting mechanism 560 isconfigured to act as a brake. In this embodiment of the transmission 500therefore two of the five torque-transmitting mechanisms are configuredto act as a brake and the other three torque-transmitting mechanisms areconfigured to act as clutches.

The third torque-transmitting mechanism 562, for example, is arrangedwithin the power flow between the input shaft 502 and the sixth shaft548. The fourth torque-transmitting mechanism 564 is arranged within thepower flow between the fourth shaft 536 and the fifth shaft 546.Moreover, the fifth torque-transmitting mechanism 566 is arranged withinthe power flow between the third shaft 526 and the fifth shaft 546.

The kinematic couplings of the embodiment in FIG. 5 can further bedescribed with respect to the selective engagement of thetorque-transmitting mechanisms with respect to one or more components ofthe plurality of planetary gearsets. For example, in the transmission500, the first torque-transmitting mechanism 558 is selectivelyengageable to couple the first sun gear 514, the second sun gear 528,and the first shaft 522 to the housing G of the transmission 500. Thesecond torque-transmitting mechanism 560 is selectively engageable tocouple the first carrier member 518 and the second shaft 522 to thehousing G of the transmission 500. Moreover, the thirdtorque-transmitting mechanism 562 is selectively engageable to coupleinput shaft 502 and the second carrier member 532 to the sixth shaft548, the third sun gear 538, and fourth sun gear 550. The fourthtorque-transmitting mechanism 564 is selectively engageable to couplefourth shaft 536, the second ring gear 530, and third ring gear 540 tothe third carrier member 542 and the fifth shaft 546. Lastly, the fifthtorque-transmitting mechanism 566 is selectively engageable to couplethe first ring gear 516, fourth ring gear 552, and the third shaft 526to the fifth shaft 546 and third carrier member 542.

Referring to FIG. 6, a schematic representation or stick diagramillustrates one embodiment of a multi-speed transmission 600 accordingto the present disclosure. The transmission 600 includes an input shaft602 and an output shaft 604. The input shaft 602 and output shaft 604can be disposed along the same axis or centerline of the transmission600. In another aspect, the different shafts can be disposed alongdifferent axes or centerlines. In a further aspect, the different shaftscan be disposed parallel to one another, but along different axes orcenterlines. Other aspect can be appreciated by one skilled in the art.

The transmission 600 can also include a plurality of planetary gearsets.In the illustrated embodiment of FIG. 6, the transmission 600 includes afirst planetary gearset 606, a second planetary gearset 608, a thirdplanetary gearset 610, and a fourth planetary gearset 612. Eachplanetary gearset can be referred to as a simple or compound planetarygearset. For example, in some aspects, one or more of the plurality ofplanetary gearsets can be formed as an idler planetary gearset. In FIG.6, for instance, the first planetary gearset 606 is structurally setforth as an idler planetary gearset. In this example, an idler planetplanetary gearset can include a sun gear, a ring gear, a carrier, andtwo sets of pinion gears. One set of pinion gears can be rotationallycoupled with the sun gear and the other set of pinion gears can berotationally coupled to the ring gear. Both sets of pinion gears arecoupled to one another such that one pinion gear of the first set isrotationally coupled to one pinion gear of the second set. In thismanner, power can be transferred through the sun or ring gear via eachof the sets of pinion gears.

One or more of the plurality of planetary gearsets can be arranged indifferent locations within the transmission 600, but for sake ofsimplicity and in this particular example only, the planetary gearsetsare aligned in an axial direction consecutively in sequence (i.e.,first, second, third, and fourth between the input and output shafts).

The transmission 600 may also include a plurality of torque-transmittingor gearshifting mechanisms. For example, one or more of these mechanismscan include a clutch or brake. In one aspect, each of the plurality ofmechanisms is disposed within an outer housing of the transmission 600.In another aspect, however, one or more of the mechanisms may bedisposed outside of the housing. Each of the plurality of mechanisms canbe coupled to one or more of the plurality of planetary gearsets, whichwill be described further below.

In the embodiment of FIG. 6, the transmission 600 can include a firsttorque-transmitting mechanism 658 and a second torque-transmittingmechanism 660 that are configured to function as brakes (e.g., thetorque-transmitting mechanism is fixedly coupled to the outer housing ofthe transmission 600). Each brake can be configured as ashiftable-friction-locked disk brake, shiftable friction-locked bandbrake, shiftable form-locking claw or conical brake, or any other typeof known brake. The transmission 600 can include a thirdtorque-transmitting mechanism 662, a fourth torque-transmittingmechanism 664, and a fifth torque-transmitting mechanism 666 that areconfigured to function as clutches. These can be shiftablefriction-locked multi-disk clutches, shiftable form-locking claw orconical clutches, wet clutches, or any other known form of a clutch.With these five torque-transmitting mechanisms, selective shifting of atleast eight forward gears and at least one reverse gear is possible.

The transmission 600 of FIG. 6 may also include up to eight differentshafts, which is inclusive of the input shaft 602 and output shaft 604.Each of these shafts, designated as a first shaft 622, a second shaft624, a third shaft 626, a fourth shaft 636, a fifth shaft 646, and asixth shaft 648, are configured to be connected to one or more of theplurality of planetary gearsets or plurality of torque-transmittingmechanism between the input shaft 602 and output shaft 604.

In FIG. 6, the first planetary gearset 606 i.e., the idler planetarygearset, can include a first sun gear 614, a first ring gear 616, and afirst carrier member 618 that rotatably supports two sets of piniongears. One set of pinion gears 668 is rotationally coupled to the sungear 614 and the other set of pinion gears 620 is rotationally coupledto the ring gear 616. The second planetary gearset 608 can include asecond sun gear 628, a second ring gear 630, and a second carrier member632 that rotatably supports a set of pinion gears 634. The thirdplanetary gearset 610 can include a third sun gear 638, a third ringgear 640, and a third carrier member 642 that rotatably supports a setof pinion gears 644. The fourth planetary gearset 612 can include afourth sun gear 650, a fourth ring gear 652, and a fourth carrier member654 that rotatably supports a set of pinion gears 656.

The transmission 600 is capable of transferring torque from the inputshaft 602 to the output shaft 604 in at least eight forward gears orratios and at least one reverse gear or ratio. Each of the forwardtorque ratios and the reverse torque ratios can be attained by theselective engagement of one or more of the torque-transmittingmechanisms (i.e., torque-transmitting mechanisms 658, 660, 662, 664, and666). Those skilled in the art will readily understand that a differentspeed ratio is associated with each torque ratio. Thus, at least eightforward speed ratios and at least one reverse speed ratio may beattained by transmission 600.

As for the transmission 600, kinematic coupling of the first planetarygearset 606 is shown in FIG. 6. The first sun gear 614 is coupled to thefirst shaft 622 for common rotation therewith. The first carrier member618 is coupled to the second shaft 624 for common rotation therewith.First ring gear 616 is coupled for common rotation with the third shaft626.

With respect to the second planetary gearset 608, the second sun gear628 is coupled to the first shaft 622 and first sun gear 614 for commonrotation therewith. The second ring gear 630 is coupled to the fourthshaft 636 for common rotation therewith. The second carrier member 632is coupled for common rotation with the input shaft 602.

The third sun gear 638 of the third planetary gearset 610 is coupled tothe sixth shaft 648 for common rotation therewith. The third ring gear640 is coupled to the fourth shaft 636 for common rotation therewith.Third pinion gears 644 are configured to intermesh with the third sungear 638 and third ring gear 640, respectively. The third carrier member642 is coupled for common rotation with the fifth shaft 646.

The kinematic relationship of the fourth planetary gearset 612 is suchthat the fourth sun gear 650 is coupled to the sixth shaft 648 forcommon rotation therewith. The fourth ring gear 652 is coupled to thethird shaft 626 for common rotation therewith. The fourth pinion gears656 are configured to intermesh with the fourth sun gear 650 and thefourth ring gear 652. The fourth carrier member 654 is coupled to theoutput shaft 604 for common rotation therewith.

With regards to the kinematic coupling of the five torque-transmittingmechanisms to the previously described shafts, the multiple speedtransmission 600 of FIG. 6 provides that the first torque-transmittingmechanism 658 is arranged within the power flow between the first shaft622 and a housing G of the transmission 600. In this manner, the firsttorque-transmitting mechanism 658 is configured to act as a brake. Thesecond torque-transmitting mechanism 660 is arranged within the powerflow between the second shaft 624 and the housing G of the transmission600. In this manner, the second torque-transmitting mechanism 660 isconfigured to act as a brake. In this embodiment of the transmission 600therefore two of the five torque-transmitting mechanisms are configuredto act as a brake and the other three torque-transmitting mechanisms areconfigured to act as clutches.

The third torque-transmitting mechanism 662, for example, is arrangedwithin the power flow between the input shaft 602 and the sixth shaft648. The fourth torque-transmitting mechanism 664 is arranged within thepower flow between the fifth shaft 646 and the sixth shaft 648.Moreover, the fifth torque-transmitting mechanism 666 is arranged withinthe power flow between the third shaft 626 and the fifth shaft 646.

The kinematic couplings of the embodiment in FIG. 6 can further bedescribed with respect to the selective engagement of thetorque-transmitting mechanisms with respect to one or more components ofthe plurality of planetary gearsets. For example, in the transmission600, the first torque-transmitting mechanism 658 is selectivelyengageable to couple the first sun gear 614, the second sun gear 628,and the first shaft 622 to the housing G of the transmission 600. Thesecond torque-transmitting mechanism 660 is selectively engageable tocouple the first carrier member 618 and the second shaft 624 to thehousing G of the transmission 600. Moreover, the thirdtorque-transmitting mechanism 662 is selectively engageable to coupleinput shaft 602 and the second carrier member 632 to the sixth shaft648, the third sun gear 638, and fourth sun gear 650. The fourthtorque-transmitting mechanism 664 is selectively engageable to couplefifth shaft 646 and the third carrier member 642 to the third sun gear638, fourth sun gear 650, and the sixth shaft 648. Lastly, the fifthtorque-transmitting mechanism 666 is selectively engageable to couplethe third shaft 626, the first ring gear 616, and the fourth ring gear652 to the fifth shaft 646 and the third carrier member 642.

Referring to FIG. 7, a schematic representation or stick diagramillustrates one embodiment of a multi-speed transmission 700 accordingto the present disclosure. The transmission 700 includes an input shaft702 and an output shaft 704. The input shaft 702 and output shaft 704can be disposed along the same axis or centerline of the transmission700. In another aspect, the different shafts can be disposed alongdifferent axes or centerlines. In a further aspect, the different shaftscan be disposed parallel to one another, but along different axes orcenterlines. Other aspect can be appreciated by one skilled in the art.

The transmission 700 can also include a plurality of planetary gearsets.In the illustrated embodiment of FIG. 7, the transmission 700 includes afirst planetary gearset 706, a second planetary gearset 708, a thirdplanetary gearset 710, and a fourth planetary gearset 712. Eachplanetary gearset can be referred to as a simple or compound planetarygearset. For example, in some aspects, one or more of the plurality ofplanetary gearsets can be formed as an idler planetary gearset. In FIG.7, for instance, the second planetary gearset 708 is structurally setforth as an idler planetary gearset. In this example, an idler planetplanetary gearset can include a sun gear, a ring gear, a carrier, andtwo sets of pinion gears. One set of pinion gears can be rotationallycoupled with the sun gear and the other set of pinion gears can berotationally coupled to the ring gear. Both sets of pinion gears arecoupled to one another such that one pinion gear of the first set isrotationally coupled to one pinion gear of the second set. In thismanner, power can be transferred through the sun or ring gear via eachof the sets of pinion gears.

One or more of the plurality of planetary gearsets can be arranged indifferent locations within the transmission 700, but for sake ofsimplicity and in this particular example only, the planetary gearsetsare aligned in an axial direction consecutively in sequence (i.e.,first, second, third, and fourth between the input and output shafts).

The transmission 700 may also include a plurality of torque-transmittingor gearshifting mechanisms. For example, one or more of these mechanismscan include a clutch or brake. In one aspect, each of the plurality ofmechanisms is disposed within an outer housing of the transmission 700.In another aspect, however, one or more of the mechanisms may bedisposed outside of the housing. Each of the plurality of mechanisms canbe coupled to one or more of the plurality of planetary gearsets, whichwill be described further below.

In the embodiment of FIG. 7, the transmission 700 can include a firsttorque-transmitting mechanism 758 and a second torque-transmittingmechanism 760 that are configured to function as brakes (e.g., thetorque-transmitting mechanism is fixedly coupled to the outer housing ofthe transmission 700). Each brake can be configured as ashiftable-friction-locked disk brake, shiftable friction-locked bandbrake, shiftable form-locking claw or conical brake, or any other typeof known brake. The transmission 700 can include a thirdtorque-transmitting mechanism 762, a fourth torque-transmittingmechanism 764, and a fifth torque-transmitting mechanism 766 that areconfigured to function as clutches. These can be shiftablefriction-locked multi-disk clutches, shiftable form-locking claw orconical clutches, wet clutches, or any other known form of a clutch.With these five torque-transmitting mechanisms, selective shifting of atleast eight forward gears and at least one reverse gear is possible.

The transmission 700 of FIG. 7 may also include up to eight differentshafts, which is inclusive of the input shaft 702 and output shaft 704.Each of these shafts, designated as a first shaft 722, a second shaft724, a third shaft 726, a fourth shaft 736, a fifth shaft 746, and asixth shaft 748, are configured to be connected to one or more of theplurality of planetary gearsets or plurality of torque-transmittingmechanism between the input shaft 702 and output shaft 704.

In FIG. 7, the first planetary gearset 706 can include a first sun gear714, a first ring gear 716, and a first carrier member 718 thatrotatably supports a set of pinion gears 720. The second planetarygearset 708, i.e., the idler planetary gearset, can include a second sungear 728, a second ring gear 730, and a second carrier member 732 thatrotatably supports two sets of pinion gears. One set of pinion gears 768is rotationally coupled to the sun gear 728 and the other set of piniongears 734 is rotationally coupled to the ring gear 730. The thirdplanetary gearset 710 can include a third sun gear 738, a third ringgear 740, and a third carrier member 742 that rotatably supports a setof pinion gears 744. The fourth planetary gearset 712 can include afourth sun gear 750, a fourth ring gear 752, and a fourth carrier member754 that rotatably supports a set of pinion gears 756.

The transmission 700 is capable of transferring torque from the inputshaft 702 to the output shaft 704 in at least eight forward gears orratios and at least one reverse gear or ratio. Each of the forwardtorque ratios and the reverse torque ratios can be attained by theselective engagement of one or more of the torque-transmittingmechanisms (i.e., torque-transmitting mechanisms 758, 760, 762, 764, and766). Those skilled in the art will readily understand that a differentspeed ratio is associated with each torque ratio. Thus, at least eightforward speed ratios and at least one reverse speed ratio may beattained by transmission 700.

As for the transmission 700, kinematic coupling of the first planetarygearset 706 is shown in FIG. 7. The first sun gear 714 is coupled to thefirst shaft 722 for common rotation therewith. The first carrier member718 is coupled to the third shaft 726 for common rotation therewith.First ring gear 716 is coupled for common rotation with the second shaft724.

With respect to the second planetary gearset 708, the second sun gear728 is coupled to the first shaft 722 and first sun gear 714 for commonrotation therewith. The second ring gear 730 is coupled to the inputshaft 702 for common rotation therewith. The second carrier member 732is coupled for common rotation with the fourth shaft 736.

The third sun gear 738 of the third planetary gearset 710 is coupled tothe sixth shaft 748 for common rotation therewith. The third ring gear740 is coupled to the fourth shaft 736 for common rotation therewith.Third pinion gears 744 are configured to intermesh with the third sungear 738 and third ring gear 740, respectively. The third carrier member742 is coupled for common rotation with the fifth shaft 746.

The kinematic relationship of the fourth planetary gearset 712 is suchthat the fourth sun gear 750 is coupled to the sixth shaft 748 forcommon rotation therewith. The fourth ring gear 752 is coupled to thethird shaft 726 for common rotation therewith. The fourth pinion gears756 are configured to intermesh with the fourth sun gear 750 and thefourth ring gear 752. The fourth carrier member 754 is coupled to theoutput shaft 704 for common rotation therewith.

With regards to the kinematic coupling of the five torque-transmittingmechanisms to the previously described shafts, the multiple speedtransmission 700 of FIG. 7 provides that the first torque-transmittingmechanism 758 is arranged within the power flow between the first shaft722 and a housing G of the transmission 700. In this manner, the firsttorque-transmitting mechanism 758 is configured to act as a brake. Thesecond torque-transmitting mechanism 760 is arranged within the powerflow between the second shaft 724 and the housing G of the transmission700. In this manner, the second torque-transmitting mechanism 760 isconfigured to act as a brake. In this embodiment of the transmission 700therefore two of the five torque-transmitting mechanisms are configuredto act as a brake and the other three torque-transmitting mechanisms areconfigured to act as clutches.

The third torque-transmitting mechanism 762, for example, is arrangedwithin the power flow between the input shaft 702 and the sixth shaft748. The fourth torque-transmitting mechanism 764 is arranged within thepower flow between the fourth shaft 736 and the sixth shaft 748.Moreover, the fifth torque-transmitting mechanism 766 is arranged withinthe power flow between the third shaft 726 and the fifth shaft 746.

The kinematic couplings of the embodiment in FIG. 7 can further bedescribed with respect to the selective engagement of thetorque-transmitting mechanisms with respect to one or more components ofthe plurality of planetary gearsets. For example, in the transmission700, the first torque-transmitting mechanism 758 is selectivelyengageable to couple the first sun gear 714, the second sun gear 728,and the first shaft 722 to the housing G of the transmission 700. Thesecond torque-transmitting mechanism 760 is selectively engageable tocouple the first ring gear 716 and the second shaft 724 to the housing Gof the transmission 700. Moreover, the third torque-transmittingmechanism 762 is selectively engageable to couple input shaft 702 andthe second ring gear 730 to the sixth shaft 748, third sun gear 738, andthe fourth sun gear 750. The fourth torque-transmitting mechanism 764 isselectively engageable to couple the third sun gear 738, the fourth sungear 750, and the sixth shaft 748 to the fourth shaft 736, the secondcarrier member 732, and the third ring gear 740. Lastly, the fifthtorque-transmitting mechanism 766 is selectively engageable to couplethe first carrier member 718, the fourth ring gear 752, and the thirdshaft 726 to the fifth shaft 746 and the third carrier member 742.

Referring to FIG. 8, a schematic representation or stick diagramillustrates one embodiment of a multi-speed transmission 800 accordingto the present disclosure. The transmission 800 includes an input shaft802 and an output shaft 804. The input shaft 802 and output shaft 804can be disposed along the same axis or centerline of the transmission800. In another aspect, the different shafts can be disposed alongdifferent axes or centerlines. In a further aspect, the different shaftscan be disposed parallel to one another, but along different axes orcenterlines. Other aspect can be appreciated by one skilled in the art.

The transmission 800 can also include a plurality of planetary gearsets.In the illustrated embodiment of FIG. 8, the transmission 800 includes afirst planetary gearset 806, a second planetary gearset 808, a thirdplanetary gearset 810, and a fourth planetary gearset 812. Eachplanetary gearset can be referred to as a simple or compound planetarygearset. For example, in some aspects, one or more of the plurality ofplanetary gearsets can be formed as an idler planetary gearset. In FIG.8, for instance, the second planetary gearset 808 is structurally setforth as an idler planetary gearset. In this example, an idler planetplanetary gearset can include a sun gear, a ring gear, a carrier, andtwo sets of pinion gears. One set of pinion gears can be rotationallycoupled with the sun gear and the other set of pinion gears can berotationally coupled to the ring gear. Both sets of pinion gears arecoupled to one another such that one pinion gear of the first set isrotationally coupled to one pinion gear of the second set. In thismanner, power can be transferred through the sun or ring gear via eachof the sets of pinion gears.

One or more of the plurality of planetary gearsets can be arranged indifferent locations within the transmission 800, but for sake ofsimplicity and in this particular example only, the planetary gearsetsare aligned in an axial direction consecutively in sequence (i.e.,first, second, third, and fourth between the input and output shafts).

The transmission 800 may also include a plurality of torque-transmittingor gearshifting mechanisms. For example, one or more of these mechanismscan include a clutch or brake. In one aspect, each of the plurality ofmechanisms is disposed within an outer housing of the transmission 800.In another aspect, however, one or more of the mechanisms may bedisposed outside of the housing. Each of the plurality of mechanisms canbe coupled to one or more of the plurality of planetary gearsets, whichwill be described further below.

In the embodiment of FIG. 8, the transmission 800 can include a firsttorque-transmitting mechanism 858 and a second torque-transmittingmechanism 860 that are configured to function as brakes (e.g., thetorque-transmitting mechanism is fixedly coupled to the outer housing ofthe transmission 800). Each brake can be configured as ashiftable-friction-locked disk brake, shiftable friction-locked bandbrake, shiftable form-locking claw or conical brake, or any other typeof known brake. The transmission 800 can include a thirdtorque-transmitting mechanism 862, a fourth torque-transmittingmechanism 864, and a fifth torque-transmitting mechanism 866 that areconfigured to function as clutches. These can be shiftablefriction-locked multi-disk clutches, shiftable form-locking claw orconical clutches, wet clutches, or any other known form of a clutch.With these five torque-transmitting mechanisms, selective shifting of atleast eight forward gears and at least one reverse gear is possible.

The transmission 800 of FIG. 8 may also include up to eight differentshafts, which is inclusive of the input shaft 802 and output shaft 804.Each of these shafts, designated as a first shaft 822, a second shaft824, a third shaft 826, a fourth shaft 836, a fifth shaft 846, and asixth shaft 848, are configured to be connected to one or more of theplurality of planetary gearsets or plurality of torque-transmittingmechanism between the input shaft 802 and output shaft 804.

In FIG. 8, the first planetary gearset 806 can include a first sun gear814, a first ring gear 816, and a first carrier member 818 thatrotatably supports a set of pinion gears 820. The second planetarygearset 808, i.e., the idler planetary gearset, can include a second sungear 828, a second ring gear 830, and a second carrier member 832 thatrotatably supports two sets of pinion gears. One set of pinion gears 868is rotationally coupled to the sun gear 828 and the other set of piniongears 834 is rotationally coupled to the ring gear 830. The thirdplanetary gearset 810 can include a third sun gear 838, a third ringgear 840, and a third carrier member 842 that rotatably supports a setof pinion gears 844. The fourth planetary gearset 812 can include afourth sun gear 850, a fourth ring gear 852, and a fourth carrier member854 that rotatably supports a set of pinion gears 856.

The transmission 800 is capable of transferring torque from the inputshaft 802 to the output shaft 804 in at least eight forward gears orratios and at least one reverse gear or ratio. Each of the forwardtorque ratios and the reverse torque ratios can be attained by theselective engagement of one or more of the torque-transmittingmechanisms (i.e., torque-transmitting mechanisms 858, 860, 862, 864, and866). Those skilled in the art will readily understand that a differentspeed ratio is associated with each torque ratio. Thus, at least eightforward speed ratios and at least one reverse speed ratio may beattained by transmission 800.

As for the transmission 800, kinematic coupling of the first planetarygearset 806 is shown in FIG. 8. The first sun gear 814 is coupled to thefirst shaft 822 for common rotation therewith. The first carrier member818 is coupled to the third shaft 826 for common rotation therewith.First ring gear 816 is coupled for common rotation with the second shaft824.

With respect to the second planetary gearset 808, the second sun gear828 is coupled to the first shaft 822 and first sun gear 814 for commonrotation therewith. The second ring gear 830 is coupled to the inputshaft 802 for common rotation therewith. The second carrier member 832is coupled for common rotation with the fourth shaft 836.

The third sun gear 838 of the third planetary gearset 810 is coupled tothe sixth shaft 848 for common rotation therewith. The third ring gear840 is coupled to the fourth shaft 836 for common rotation therewith.Third pinion gears 844 are configured to intermesh with the third sungear 838 and third ring gear 840, respectively. The third carrier member842 is coupled for common rotation with the fifth shaft 846.

The kinematic relationship of the fourth planetary gearset 812 is suchthat the fourth sun gear 850 is coupled to the sixth shaft 848 forcommon rotation therewith. The fourth ring gear 852 is coupled to thethird shaft 826 for common rotation therewith. The fourth pinion gears856 are configured to intermesh with the fourth sun gear 850 and thefourth ring gear 852. The fourth carrier member 854 is coupled to theoutput shaft 804 for common rotation therewith.

With regards to the kinematic coupling of the five torque-transmittingmechanisms to the previously described shafts, the multiple speedtransmission 800 of FIG. 8 provides that the first torque-transmittingmechanism 858 is arranged within the power flow between the first shaft822 and a housing G of the transmission 800. In this manner, the firsttorque-transmitting mechanism 858 is configured to act as a brake. Thesecond torque-transmitting mechanism 860 is arranged within the powerflow between the second shaft 824 and the housing G of the transmission800. In this manner, the second torque-transmitting mechanism 860 isconfigured to act as a brake. In this embodiment of the transmission 800therefore two of the five torque-transmitting mechanisms are configuredto act as a brake and the other three torque-transmitting mechanisms areconfigured to act as clutches.

The third torque-transmitting mechanism 862, for example, is arrangedwithin the power flow between the input shaft 802 and the sixth shaft848. The fourth torque-transmitting mechanism 864 is arranged within thepower flow between the fourth shaft 836 and the fifth shaft 846.Moreover, the fifth torque-transmitting mechanism 866 is arranged withinthe power flow between the third shaft 826 and the fifth shaft 846.

The kinematic couplings of the embodiment in FIG. 8 can further bedescribed with respect to the selective engagement of thetorque-transmitting mechanisms with respect to one or more components ofthe plurality of planetary gearsets. For example, in the transmission800, the first torque-transmitting mechanism 858 is selectivelyengageable to couple the first sun gear 814, the second sun gear 828,and the first shaft 822 to the housing G of the transmission 800. Thesecond torque-transmitting mechanism 860 is selectively engageable tocouple the first ring gear 816 and the second shaft 824 to the housing Gof the transmission 800. Moreover, the third torque-transmittingmechanism 862 is selectively engageable to couple input shaft 802 andthe second ring gear 830 to the sixth shaft 848, the third sun gear 838,and fourth sun gear 850. The fourth torque-transmitting mechanism 864 isselectively engageable to couple the second carrier member 832, thethird ring gear 840, and the fourth shaft 836 to the fifth shaft 846 andthird carrier member 842. Lastly, the fifth torque-transmittingmechanism 866 is selectively engageable to couple the first carriermember 818, the fourth ring gear 852, and the third shaft 826 to thefifth shaft 846 and third carrier member 842.

Referring to FIG. 9, a schematic representation or stick diagramillustrates another embodiment of a multi-speed transmission 900according to the present disclosure. The transmission 900 includes aninput shaft 902 and an output shaft 904. The input shaft 902 and outputshaft 904 can be disposed along the same axis or centerline of thetransmission 900. In another aspect, the different shafts can bedisposed along different axes or centerlines. In a further aspect, thedifferent shafts can be disposed parallel to one another, but alongdifferent axes or centerlines. Other aspect can be appreciated by oneskilled in the art.

The transmission 900 can also include a plurality of planetary gearsets.In the illustrated embodiment of FIG. 9, the transmission 900 includes afirst planetary gearset 906, a second planetary gearset 908, a thirdplanetary gearset 910, and a fourth planetary gearset 912. Eachplanetary gearset can be referred to as a simple or compound planetarygearset. For example, in some aspects, one or more of the plurality ofplanetary gearsets can be formed as an idler planetary gearset. In FIG.9, for instance, the second planetary gearset 908 is structurally setforth as an idler planetary gearset. In this example, an idler planetplanetary gearset can include a sun gear, a ring gear, a carrier, andtwo sets of pinion gears. One set of pinion gears can be rotationallycoupled with the sun gear and the other set of pinion gears can berotationally coupled to the ring gear. Both sets of pinion gears arecoupled to one another such that one pinion gear of the first set isrotationally coupled to one pinion gear of the second set. In thismanner, power can be transferred through the sun or ring gear via eachof the sets of pinion gears.

One or more of the plurality of planetary gearsets can be arranged indifferent locations within the transmission 900, but for sake ofsimplicity and in this particular example only, the planetary gearsetsare aligned in an axial direction consecutively in sequence (i.e.,first, second, third, and fourth between the input and output shafts).

The transmission 900 may also include a plurality of torque-transmittingor gearshifting mechanisms. For example, one or more of these mechanismscan include a clutch or brake. In one aspect, each of the plurality ofmechanisms is disposed within an outer housing of the transmission 900.In another aspect, however, one or more of the mechanisms may bedisposed outside of the housing. Each of the plurality of mechanisms canbe coupled to one or more of the plurality of planetary gearsets, whichwill be described further below.

In the embodiment of FIG. 9, the transmission 900 can include a firsttorque-transmitting mechanism 958 and a second torque-transmittingmechanism 960 that are configured to function as brakes (e.g., thetorque-transmitting mechanism is fixedly coupled to the outer housing ofthe transmission 900). Each brake can be configured as ashiftable-friction-locked disk brake, shiftable friction-locked bandbrake, shiftable form-locking claw or conical brake, or any other typeof known brake. The transmission 900 can include a thirdtorque-transmitting mechanism 962, a fourth torque-transmittingmechanism 964, and a fifth torque-transmitting mechanism 966 that areconfigured to function as clutches. These can be shiftablefriction-locked multi-disk clutches, shiftable form-locking claw orconical clutches, wet clutches, or any other known form of a clutch.With these five torque-transmitting mechanisms, selective shifting of atleast eight forward gears and at least one reverse gear is possible.

The transmission 900 of FIG. 9 may also include up to eight differentshafts, which is inclusive of the input shaft 902 and output shaft 904.Each of these shafts, designated as a first shaft 922, a second shaft924, a third shaft 926, a fourth shaft 936, a fifth shaft 946, and asixth shaft 948, are configured to be connected to one or more of theplurality of planetary gearsets or plurality of torque-transmittingmechanism between the input shaft 902 and output shaft 904.

In FIG. 9, the first planetary gearset 906 can include a first sun gear914, a first ring gear 916, and a first carrier member 918 thatrotatably supports a set of pinion gears 920. The second planetarygearset 908, i.e., the idler planetary gearset, can include a second sungear 928, a second ring gear 930, and a second carrier member 932 thatrotatably supports two sets of pinion gears. One set of pinion gears 968is rotationally coupled to the sun gear 928 and the other set of piniongears 934 is rotationally coupled to the ring gear 930. The thirdplanetary gearset 910 can include a third sun gear 938, a third ringgear 940, and a third carrier member 942 that rotatably supports a setof pinion gears 944. The fourth planetary gearset 912 can include afourth sun gear 950, a fourth ring gear 952, and a fourth carrier member954 that rotatably supports a set of pinion gears 956.

The transmission 900 is capable of transferring torque from the inputshaft 902 to the output shaft 904 in at least eight forward gears orratios and at least one reverse gear or ratio. Each of the forwardtorque ratios and the reverse torque ratios can be attained by theselective engagement of one or more of the torque-transmittingmechanisms (i.e., torque-transmitting mechanisms 958, 960, 962, 964, and966). Those skilled in the art will readily understand that a differentspeed ratio is associated with each torque ratio. Thus, at least eightforward speed ratios and at least one reverse speed ratio may beattained by transmission 900.

As for the transmission 900, kinematic coupling of the first planetarygearset 906 is shown in FIG. 9. The first sun gear 914 is coupled to thefirst shaft 922 for common rotation therewith. The first carrier member918 is coupled to the third shaft 926 for common rotation therewith.First ring gear 916 is coupled for common rotation with the second shaft924.

With respect to the second planetary gearset 908, the second sun gear928 is coupled to the first shaft 922 and first sun gear 914 for commonrotation therewith. The second ring gear 930 is coupled to the inputshaft 902 for common rotation therewith. The second carrier member 932is coupled for common rotation with the fourth shaft 936.

The third sun gear 938 of the third planetary gearset 910 is coupled tothe sixth shaft 948 for common rotation therewith. The third ring gear940 is coupled to the fourth shaft 936 for common rotation therewith.Third pinion gears 944 are configured to intermesh with the third sungear 938 and third ring gear 940, respectively. The third carrier member942 is coupled for common rotation with the fifth shaft 946.

The kinematic relationship of the fourth planetary gearset 912 is suchthat the fourth sun gear 950 is coupled to the sixth shaft 948 and thirdsun gear 938 for common rotation therewith. The fourth ring gear 952 iscoupled to the third shaft 926 and first carrier member 918 for commonrotation therewith. The fourth pinion gears 956 are configured tointermesh with the fourth sun gear 950 and the fourth ring gear 952. Thefourth carrier member 954 is coupled to the output shaft 904 for commonrotation therewith.

With regards to the kinematic coupling of the five torque-transmittingmechanisms to the previously described shafts, the multiple speedtransmission 900 of FIG. 9 provides that the first torque-transmittingmechanism 958 is arranged within the power flow between the first shaft922 and a housing G of the transmission 900. In this manner, the firsttorque-transmitting mechanism 958 is configured to act as a brake. Thesecond torque-transmitting mechanism 960 is arranged within the powerflow between the second shaft 924 and the housing G of the transmission900. In this manner, the second torque-transmitting mechanism 960 isconfigured to act as a brake. In this embodiment of the transmission 900therefore two of the five torque-transmitting mechanisms are configuredto act as a brake and the other three torque-transmitting mechanisms areconfigured to act as clutches.

The third torque-transmitting mechanism 962, for example, is arrangedwithin the power flow between the input shaft 902 and the sixth shaft948. The fourth torque-transmitting mechanism 964 is arranged within thepower flow between the fifth shaft 946 and the sixth shaft 948.Moreover, the fifth torque-transmitting mechanism 966 is arranged withinthe power flow between the third shaft 926 and the fifth shaft 946.

The kinematic couplings of the embodiment in FIG. 9 can further bedescribed with respect to the selective engagement of thetorque-transmitting mechanisms with respect to one or more components ofthe plurality of planetary gearsets. For example, in the transmission900, the first torque-transmitting mechanism 958 is selectivelyengageable to couple the first sun gear 914, the second sun gear 928,and the first shaft 922 to the housing G of the transmission 900. Thesecond torque-transmitting mechanism 960 is selectively engageable tocouple the first ring gear 916 and the second shaft 924 to the housing Gof the transmission 900. Moreover, the third torque-transmittingmechanism 962 is selectively engageable to couple input shaft 902 andthe second ring gear 930 to the sixth shaft 948, the third sun gear 938,and fourth sun gear 950. The fourth torque-transmitting mechanism 964 isselectively engageable to couple the third carrier member 942 and thefifth shaft 946 to the sixth shaft 948, the third sun gear 938, andfourth sun gear 950. Lastly, the fifth torque-transmitting mechanism 966is selectively engageable to couple the first carrier member 918, thefourth ring gear 952, and the third shaft 926 to the fifth shaft 946 andthe third carrier member 942.

Referring to FIG. 10, a schematic representation or stick diagramillustrates a different embodiment of a multi-speed transmission 1000according to the present disclosure. The transmission 1000 includes aninput shaft 1002 and an output shaft 1004. The input shaft 1002 andoutput shaft 1004 can be disposed along the same axis or centerline ofthe transmission 1000. In another aspect, the different shafts can bedisposed along different axes or centerlines. In a further aspect, thedifferent shafts can be disposed parallel to one another, but alongdifferent axes or centerlines. Other aspect can be appreciated by oneskilled in the art.

The transmission 1000 can also include a plurality of planetarygearsets. In the illustrated embodiment of FIG. 10, the transmission1000 includes a first planetary gearset 1006, a second planetary gearset1008, a third planetary gearset 1010, and a fourth planetary gearset1012. Each planetary gearset can be referred to as a simple or compoundplanetary gearset. For example, in some aspects, one or more of theplurality of planetary gearsets can be formed as an idler planetarygearset. In FIG. 10, for instance, the third planetary gearset 1010 isstructurally set forth as an idler planetary gearset. In this example,an idler planet planetary gearset can include a sun gear, a ring gear, acarrier, and two sets of pinion gears. One set of pinion gears can berotationally coupled with the sun gear and the other set of pinion gearscan be rotationally coupled to the ring gear. Both sets of pinion gearsare coupled to one another such that one pinion gear of the first set isrotationally coupled to one pinion gear of the second set. In thismanner, power can be transferred through the sun or ring gear via eachof the sets of pinion gears.

One or more of the plurality of planetary gearsets can be arranged indifferent locations within the transmission 1000, but for sake ofsimplicity and in this particular example only, the planetary gearsetsare aligned in an axial direction consecutively in sequence (i.e.,first, second, third, and fourth between the input and output shafts).

The transmission 1000 may also include a plurality oftorque-transmitting or gearshifting mechanisms. For example, one or moreof these mechanisms can include a clutch or brake. In one aspect, eachof the plurality of mechanisms is disposed within an outer housing ofthe transmission 1000. In another aspect, however, one or more of themechanisms may be disposed outside of the housing. Each of the pluralityof mechanisms can be coupled to one or more of the plurality ofplanetary gearsets, which will be described further below.

In the embodiment of FIG. 10, the transmission 1000 can include a firsttorque-transmitting mechanism 1058 and a second torque-transmittingmechanism 1060 that are configured to function as brakes (e.g., thetorque-transmitting mechanism is fixedly coupled to the outer housing ofthe transmission 1000). Each brake can be configured as ashiftable-friction-locked disk brake, shiftable friction-locked bandbrake, shiftable form-locking claw or conical brake, or any other typeof known brake. The transmission 1000 can include a thirdtorque-transmitting mechanism 1062, a fourth torque-transmittingmechanism 1064, and a fifth torque-transmitting mechanism 1066 that areconfigured to function as clutches. These can be shiftablefriction-locked multi-disk clutches, shiftable form-locking claw orconical clutches, wet clutches, or any other known form of a clutch.With these five torque-transmitting mechanisms, selective shifting of atleast eight forward gears and at least one reverse gear is possible.

The transmission 1000 of FIG. 10 may also include up to eight differentshafts, which is inclusive of the input shaft 1002 and output shaft1004. Each of these shafts, designated as a first shaft 1022, a secondshaft 1024, a third shaft 1026, a fourth shaft 1036, a fifth shaft 1046,and a sixth shaft 1048, are configured to be connected to one or more ofthe plurality of planetary gearsets or plurality of torque-transmittingmechanism between the input shaft 1002 and output shaft 1004.

In FIG. 10, the first planetary gearset 1006 can include a first sungear 1014, a first ring gear 1016, and a first carrier member 1018 thatrotatably supports a set of pinion gears 1020. The second planetarygearset 1008 can include a second sun gear 1028, a second ring gear1030, and a second carrier member 1032 that rotatably supports a set ofpinion gears 1034. The third planetary gearset 1010, i.e., the idlerplanetary gearset, can include a third sun gear 1038, a third ring gear1040, and a third carrier member 1042 that rotatably supports two setsof pinion gears. One set of pinion gears 1068 is rotationally coupled tothe sun gear 1038 and the other set of pinion gears 1044 is rotationallycoupled to the ring gear 1040. The fourth planetary gearset 1012 caninclude a fourth sun gear 1050, a fourth ring gear 1052, and a fourthcarrier member 1054 that rotatably supports a set of pinion gears 1056.

The transmission 1000 is capable of transferring torque from the inputshaft 1002 to the output shaft 1004 in at least eight forward gears orratios and at least one reverse gear or ratio. Each of the forwardtorque ratios and the reverse torque ratios can be attained by theselective engagement of one or more of the torque-transmittingmechanisms (i.e., torque-transmitting mechanisms 1058, 1060, 1062, 1064,and 1066). Those skilled in the art will readily understand that adifferent speed ratio is associated with each torque ratio. Thus, atleast eight forward speed ratios and at least one reverse speed ratiomay be attained by transmission 1000.

As for the transmission 1000, kinematic coupling of the first planetarygearset 1006 is shown in FIG. 10. The first sun gear 1014 is coupled tothe first shaft 1022 for common rotation therewith. The first carriermember 1018 is coupled to the third shaft 1026 for common rotationtherewith. First ring gear 1016 is coupled for common rotation with thesecond shaft 1024.

With respect to the second planetary gearset 1008, the second sun gear1028 is coupled to the first shaft 1022 and first sun gear 1014 forcommon rotation therewith. The second ring gear 1030 is coupled to thefourth shaft 1036 for common rotation therewith. The second carriermember 1032 is coupled for common rotation with the input shaft 1002.

The third sun gear 1038 of the third planetary gearset 1010 is coupledto the sixth shaft 1048 for common rotation therewith. The third ringgear 1040 is coupled to the fifth shaft 1046 for common rotationtherewith. The third carrier member 1042 is coupled for common rotationwith the fourth shaft 1036.

The kinematic relationship of the fourth planetary gearset 1012 is suchthat the fourth sun gear 1050 is coupled to the sixth shaft 1048 forcommon rotation therewith. The fourth ring gear 1052 is coupled to thethird shaft 1026 and the first carrier member 1018 for common rotationtherewith. The fourth pinion gears 1056 are configured to intermesh withthe fourth sun gear 1050 and the fourth ring gear 1052. The fourthcarrier member 1054 is coupled to the output shaft 1004 for commonrotation therewith.

With regards to the kinematic coupling of the five torque-transmittingmechanisms to the previously described shafts, the multiple speedtransmission 1000 of FIG. 10 provides that the first torque-transmittingmechanism 1058 is arranged within the power flow between the first shaft1022 and a housing G of the transmission 1000. In this manner, the firsttorque-transmitting mechanism 1058 is configured to act as a brake. Thesecond torque-transmitting mechanism 1060 is arranged within the powerflow between the second shaft 1024 and the housing G of the transmission1000. In this manner, the second torque-transmitting mechanism 1060 isconfigured to act as a brake. In this embodiment of the transmission1000 therefore two of the five torque-transmitting mechanisms areconfigured to act as a brake and the other three torque-transmittingmechanisms are configured to act as clutches.

The third torque-transmitting mechanism 1062, for example, is arrangedwithin the power flow between the input shaft 1002 and the sixth shaft1048. The fourth torque-transmitting mechanism 1064 is arranged withinthe power flow between the fourth shaft 1036 and the fifth shaft 1046.Moreover, the fifth torque-transmitting mechanism 1066 is arrangedwithin the power flow between the third shaft 1026 and the fifth shaft1046.

The kinematic couplings of the embodiment in FIG. 10 can further bedescribed with respect to the selective engagement of thetorque-transmitting mechanisms with respect to one or more components ofthe plurality of planetary gearsets. For example, in the transmission1000, the first torque-transmitting mechanism 1058 is selectivelyengageable to couple the first sun gear 1014, the second sun gear 1028,and the first shaft 1022 to the housing G of the transmission 1000. Thesecond torque-transmitting mechanism 1060 is selectively engageable tocouple the first ring gear 1016 and the second shaft 1024 to the housingG of the transmission 1000. Moreover, the third torque-transmittingmechanism 1062 is selectively engageable to couple input shaft 1002 andthe second carrier member 1032 to the sixth shaft 1048, the third sungear 1038, and fourth sun gear 1050. The fourth torque-transmittingmechanism 1064 is selectively engageable to couple the third ring gear1040 and the fifth shaft 1046 to the fourth shaft 1036 and third carriermember 1042. Lastly, the fifth torque-transmitting mechanism 1066 isselectively engageable to couple the first carrier member 1018, thefourth ring gear 1052, and the third shaft 1026 to the fifth shaft 1046and third ring gear 1040.

Referring to FIG. 11, a schematic representation or stick diagramillustrates a further embodiment of a multi-speed transmission 1100according to the present disclosure. The transmission 1100 includes aninput shaft 1102 and an output shaft 1104. The input shaft 1102 andoutput shaft 1104 can be disposed along the same axis or centerline ofthe transmission 1100. In another aspect, the different shafts can bedisposed along different axes or centerlines. In a further aspect, thedifferent shafts can be disposed parallel to one another, but alongdifferent axes or centerlines. Other aspect can be appreciated by oneskilled in the art.

The transmission 1100 can also include a plurality of planetarygearsets. In the illustrated embodiment of FIG. 11, the transmission1100 includes a first planetary gearset 1106, a second planetary gearset1108, a third planetary gearset 1110, and a fourth planetary gearset1112. Each planetary gearset can be referred to as a simple or compoundplanetary gearset. For example, in some aspects, one or more of theplurality of planetary gearsets can be formed as an idler planetarygearset. In FIG. 11, for instance, the third planetary gearset 1110 isstructurally set forth as an idler planetary gearset. In this example,an idler planet planetary gearset can include a sun gear, a ring gear, acarrier, and two sets of pinion gears. One set of pinion gears can berotationally coupled with the sun gear and the other set of pinion gearscan be rotationally coupled to the ring gear. Both sets of pinion gearsare coupled to one another such that one pinion gear of the first set isrotationally coupled to one pinion gear of the second set. In thismanner, power can be transferred through the sun or ring gear via eachof the sets of pinion gears.

One or more of the plurality of planetary gearsets can be arranged indifferent locations within the transmission 1100, but for sake ofsimplicity and in this particular example only, the planetary gearsetsare aligned in an axial direction consecutively in sequence (i.e.,first, second, third, and fourth between the input and output shafts).

The transmission 1100 may also include a plurality oftorque-transmitting or gearshifting mechanisms. For example, one or moreof these mechanisms can include a clutch or brake. In one aspect, eachof the plurality of mechanisms is disposed within an outer housing ofthe transmission 1100. In another aspect, however, one or more of themechanisms may be disposed outside of the housing. Each of the pluralityof mechanisms can be coupled to one or more of the plurality ofplanetary gearsets, which will be described further below.

In the embodiment of FIG. 11, the transmission 1100 can include a firsttorque-transmitting mechanism 1158 and a second torque-transmittingmechanism 1160 that are configured to function as brakes (e.g., thetorque-transmitting mechanism is fixedly coupled to the outer housing ofthe transmission 1100). Each brake can be configured as ashiftable-friction-locked disk brake, shiftable friction-locked bandbrake, shiftable form-locking claw or conical brake, or any other typeof known brake. The transmission 1100 can include a thirdtorque-transmitting mechanism 1162, a fourth torque-transmittingmechanism 1164, and a fifth torque-transmitting mechanism 1166 that areconfigured to function as clutches. These can be shiftablefriction-locked multi-disk clutches, shiftable form-locking claw orconical clutches, wet clutches, or any other known form of a clutch.With these five torque-transmitting mechanisms, selective shifting of atleast eight forward gears and at least one reverse gear is possible.

The transmission 1100 of FIG. 11 may also include up to eight differentshafts, which is inclusive of the input shaft 1102 and output shaft1104. Each of these shafts, designated as a first shaft 1122, a secondshaft 1124, a third shaft 1126, a fourth shaft 1136, a fifth shaft 1146,and a sixth shaft 1148, are configured to be connected to one or more ofthe plurality of planetary gearsets or plurality of torque-transmittingmechanism between the input shaft 1102 and output shaft 1104.

In FIG. 11, the first planetary gearset 1106 can include a first sungear 1114, a first ring gear 1116, and a first carrier member 1118 thatrotatably supports a set of pinion gears 1120. The second planetarygearset 1108 can include a second sun gear 1128, a second ring gear1130, and a second carrier member 1132 that rotatably supports a set ofpinion gears 1134. The third planetary gearset 1110, i.e., the idlerplanetary gearset, can include a third sun gear 1138, a third ring gear1140, and a third carrier member 1142 that rotatably supports two setsof pinion gears. One set of pinion gears 1168 is rotationally coupled tothe sun gear 1138 and the other set of pinion gears 1144 is rotationallycoupled to the ring gear 1140. The fourth planetary gearset 1112 caninclude a fourth sun gear 1150, a fourth ring gear 1152, and a fourthcarrier member 1154 that rotatably supports a set of pinion gears 1156.

The transmission 1100 is capable of transferring torque from the inputshaft 1102 to the output shaft 1104 in at least eight forward gears orratios and at least one reverse gear or ratio. Each of the forwardtorque ratios and the reverse torque ratios can be attained by theselective engagement of one or more of the torque-transmittingmechanisms (i.e., torque-transmitting mechanisms 1158, 1160, 1162, 1164,and 1166). Those skilled in the art will readily understand that adifferent speed ratio is associated with each torque ratio. Thus, atleast eight forward speed ratios and at least one reverse speed ratiomay be attained by transmission 1100.

As for the transmission 1100, kinematic coupling of the first planetarygearset 1106 is shown in FIG. 11. The first sun gear 1114 is coupled tothe first shaft 1122 for common rotation therewith. The first carriermember 1118 is coupled to the third shaft 1126 for common rotationtherewith. First ring gear 1116 is coupled for common rotation with thesecond shaft 1124.

With respect to the second planetary gearset 1108, the second sun gear1128 is coupled to the first shaft 1122 and first sun gear 1114 forcommon rotation therewith. The second ring gear 1130 is coupled to thefourth shaft 1136 for common rotation therewith. The second carriermember 1132 is coupled for common rotation with the input shaft 1102.

The third sun gear 1138 of the third planetary gearset 1110 is coupledto the sixth shaft 1148 for common rotation therewith. The third ringgear 1140 is coupled to the fifth shaft 1146 for common rotationtherewith. The third carrier member 1142 is coupled for common rotationwith the fourth shaft 1136.

The kinematic relationship of the fourth planetary gearset 1112 is suchthat the fourth sun gear 1150 is coupled to the sixth shaft 1148 forcommon rotation therewith. The fourth ring gear 1152 is coupled to thethird shaft 1126 and the first carrier member 1118 for common rotationtherewith. The fourth pinion gears 1156 are configured to intermesh withthe fourth sun gear 1150 and the fourth ring gear 1152. The fourthcarrier member 1154 is coupled to the output shaft 1104 for commonrotation therewith.

With regards to the kinematic coupling of the five torque-transmittingmechanisms to the previously described shafts, the multiple speedtransmission 1100 of FIG. 11 provides that the first torque-transmittingmechanism 1158 is arranged within the power flow between the first shaft1122 and a housing G of the transmission 1100. In this manner, the firsttorque-transmitting mechanism 1158 is configured to act as a brake. Thesecond torque-transmitting mechanism 1160 is arranged within the powerflow between the second shaft 1124 and the housing G of the transmission1100. In this manner, the second torque-transmitting mechanism 1160 isconfigured to act as a brake. In this embodiment of the transmission1100 therefore two of the five torque-transmitting mechanisms areconfigured to act as a brake and the other three torque-transmittingmechanisms are configured to act as clutches.

The third torque-transmitting mechanism 1162, for example, is arrangedwithin the power flow between the input shaft 1102 and the sixth shaft1148. The fourth torque-transmitting mechanism 1164 is arranged withinthe power flow between the fifth shaft 1146 and the sixth shaft 1148.Moreover, the fifth torque-transmitting mechanism 1166 is arrangedwithin the power flow between the third shaft 1126 and the fifth shaft1146.

The kinematic couplings of the embodiment in FIG. 11 can further bedescribed with respect to the selective engagement of thetorque-transmitting mechanisms with respect to one or more components ofthe plurality of planetary gearsets. For example, in the transmission1100, the first torque-transmitting mechanism 1158 is selectivelyengageable to couple the first sun gear 1114, the second sun gear 1128,and the first shaft 1122 to the housing G of the transmission 1100. Thesecond torque-transmitting mechanism 1160 is selectively engageable tocouple the first ring gear 1116 and the second shaft 1124 to the housingG of the transmission 1100. Moreover, the third torque-transmittingmechanism 1162 is selectively engageable to couple input shaft 1102 andthe second carrier member 1132 to the sixth shaft 1148, the third sungear 1138, and fourth sun gear 1150. The fourth torque-transmittingmechanism 1164 is selectively engageable to couple the third ring gear1140 and the fifth shaft 1146 to the sixth shaft 1148, the third sungear 1138, and fourth sun gear 1150. Lastly, the fifthtorque-transmitting mechanism 1166 is selectively engageable to couplethe first carrier member 1118, the fourth ring gear 1152, and the thirdshaft 1126 to the fifth shaft 1146 and third ring gear 1140.

As previously described, the aforementioned embodiment is capable oftransmitting torque from a respective input shaft to a respective outputshaft in at least eight forward torque ratios and one reverse torqueratio. Referring to FIG. 12, one example of a truth table is shownrepresenting a state of engagement of various torque transmittingmechanisms in each of the available forward and reverse speeds or gearratios of the transmissions illustrated in FIGS. 2-11. It is to beunderstood that FIG. 12 is only one example of any number of truthtables possible for achieving at least eight forward ratios and onereverse ratio, and one skilled in the art is capable of configuringdiameters, gear tooth counts, and gear configurations to achieve otherratios.

In the example of FIG. 12, the reverse ratio (rev) can be achieved bythe selective engagement of the torque-transmitting mechanisms as setforth in the table. As shown, the first torque transmitting mechanism(B1), second torque-transmitting mechanism (B2), and fifthtorque-transmitting mechanism (C5) are selectively engaged to establishthe reverse ratio. Thus, in transmission 200 of FIG. 2, the selectiveengagement of mechanisms 258, 260, and 266 can establish the reverseratio.

In neutral (Neu), none of the torque-transmitting mechanisms carrytorque. One or more of the torque-transmitting mechanisms, however, maybe engaged in neutral but not carrying torque. For example, the firstand fourth torque-transmitting mechanisms can be engaged in neutral,thereby resulting in the fifth torque-transmitting mechanism beingdisengaged between a shift between the one reverse ratio and neutral.

A first forward ratio (shown as 1st) in the table of FIG. 12 is achievedby engaging both brakes and one of the clutches. In FIG. 2, for example,the first torque-transmitting mechanism 258, the secondtorque-transmitting mechanism 260, and the third torque-transmittingmechanism 262 are engaged. Thus, when transitioning between neutral andthe first forward range, the first and second torque-transmittingmechanisms may already be engaged, and the third torque-transmittingmechanism is selectively engaged.

In a second or subsequent forward ratio, indicated as 2nd in FIG. 12,the first torque-transmitting mechanism, the second torque-transmittingmechanism, and the fourth torque-transmitting mechanism are selectivelyengaged. Therefore, when transitioning between the first forward ratioand the second forward ratio, the third torque-transmitting mechanism isreleased and the fourth torque-transmitting mechanism is engaged.

In a third or subsequent forward ratio, indicated as 3rd forward ratioin FIG. 12, the second torque-transmitting mechanism, thirdtorque-transmitting mechanism, and fourth torque-transmitting mechanismare engaged. To transition from the second forward ratio to the thirdforward ratio, for example, the first torque-transmitting mechanism isreleased and the third torque-transmitting mechanism is engaged.

In a fourth or the next subsequent forward ratio, indicated as 4th inFIG. 12, the second torque-transmitting mechanism, fourthtorque-transmitting mechanism, and fifth torque-transmitting mechanismare engaged. Thus, to transition from the third forward ratio andupshift to the fourth forward ratio, the third torque-transmittingmechanism is released and the fifth torque-transmitting mechanism isengaged.

In a fifth or the next subsequent forward ratio, indicated as 5th inFIG. 12, the second torque-transmitting mechanism, thirdtorque-transmitting mechanism, and fifth torque-transmitting mechanismare engaged. Thus, to transition from the fourth forward ratio andupshift to the fifth forward ratio, the fourth torque-transmittingmechanism is released and the third torque-transmitting mechanism isengaged.

In a sixth or the next subsequent forward ratio, indicated as 6th inFIG. 12, the third torque-transmitting mechanism, fourthtorque-transmitting mechanism, and fifth torque-transmitting mechanismare engaged. Thus, to transition from the fifth forward ratio andupshift to the sixth forward ratio, the second torque-transmittingmechanism is released and the fourth torque-transmitting mechanism isengaged.

In a seventh or the next subsequent forward ratio, indicated as 7th inFIG. 12, the first torque-transmitting mechanism, thirdtorque-transmitting mechanism, and fifth torque-transmitting mechanismare engaged. Thus, to transition from the sixth forward ratio andupshift to the seventh forward ratio, the fourth torque-transmittingmechanism is released and the first torque-transmitting mechanism isengaged.

In an eighth or the next subsequent forward ratio, indicated as 8th inFIG. 12, the first torque-transmitting mechanism, fourthtorque-transmitting mechanism, and fifth torque-transmitting mechanismare engaged. Thus, to transition from the seventh forward ratio andupshift to the eighth forward ratio, the third torque-transmittingmechanism is released and the fourth torque-transmitting mechanism isengaged.

The present disclosure contemplates that downshifts follow the reversesequence of the corresponding upshift (as described above), and severalpower-on skip-shifts that are single-transition are possible (e.g. from1st to 3rd or 3rd to 1st).

While exemplary embodiments incorporating the principles of the presentdisclosure have been disclosed hereinabove, the present disclosure isnot limited to the disclosed embodiments. Instead, this application isintended to cover any variations, uses, or adaptations of the disclosureusing its general principles. Further, this application is intended tocover such departures from the present disclosure as come within knownor customary practice in the art to which this disclosure pertains andwhich fall within the limits of the appended claims.

The invention claimed is:
 1. A multiple speed transmission, comprising:an input member; an output member; first, second, third and fourthplanetary gearsets each having first, second and third members; aplurality of interconnecting members each connected between at least oneof the first, second, third, and fourth planetary gearsets and at leastanother of the first, second, third, and fourth planetary gearsets; afirst torque-transmitting mechanism selectively engageable tointerconnect the first member of the first planetary gearset and thefirst member of the second planetary gearset with a stationary member; asecond torque-transmitting mechanism selectively engageable tointerconnect the third member of the first planetary gearset with thestationary member; a third torque-transmitting mechanism selectivelyengageable to interconnect the second member of the second planetarygearset with the first member of the third planetary gearset and thefirst member of the fourth planetary gearset; a fourthtorque-transmitting mechanism selectively engageable to interconnect thethird member of the third planetary gearset with the third member of thesecond planetary gearset and the second member of the third planetarygearset; and a fifth torque-transmitting mechanism selectivelyengageable to interconnect the second member of the first planetarygearset and the third member of the fourth planetary gearset with thethird member of the third planetary gearset; wherein, the thirdplanetary gearset comprises an idler planetary gearset; wherein thetorque transmitting mechanisms are selectively engageable incombinations of at least three to establish at least eight forward speedratios and at least one reverse speed ratio between the input member andthe output member.
 2. The multiple speed transmission of claim 1,wherein the input member is continuously interconnected with the secondmember of the second planetary gearset.
 3. The multiple speedtransmission of claim 1, wherein the output member is continuouslyinterconnected with the second member of the fourth planetary gearset.4. The multiple speed transmission of claim 1, wherein the plurality ofinterconnecting members includes a first interconnecting membercontinuously interconnecting the first member of the first planetarygearset with the first member of the second planetary gearset.
 5. Themultiple speed transmission of claim 1, wherein the plurality ofinterconnecting members includes a second interconnecting memberdirectly connected to the third member of the first planetary gearset.6. The multiple speed transmission of claim 1, wherein the plurality ofinterconnecting members includes a third interconnecting membercontinuously interconnecting the second member of the first planetarygearset with the third member of the fourth planetary gearset.
 7. Themultiple speed transmission of claim 1, wherein the plurality ofinterconnecting members includes a fourth interconnecting membercontinuously interconnecting the third member of the second planetarygearset with the second member of the third planetary gearset.
 8. Themultiple speed transmission of claim 1, wherein the plurality ofinterconnecting members includes a fifth interconnecting member directlyconnected to the third member of the third planetary gearset.
 9. Themultiple speed transmission of claim 1, wherein the plurality ofinterconnecting members includes a sixth interconnecting membercontinuously interconnecting the first member of the third planetarygearset with the first member of the fourth planetary gearset.
 10. Amultiple speed transmission, comprising: an input member; an outputmember; first, second, third and fourth planetary gearsets each having asun gear, a ring gear, and a carrier member; a plurality ofinterconnecting members each connected between at least one of thefirst, second, third, and fourth planetary gearsets and at least anotherof the first, second, third, and fourth planetary gearsets; a firsttorque-transmitting mechanism selectively engageable to interconnect thesun gear of the first planetary gearset and the sun gear of the secondplanetary gearset with a stationary member; a second torque-transmittingmechanism selectively engageable to interconnect the ring gear of thefirst planetary gearset with the stationary member; a thirdtorque-transmitting mechanism selectively engageable to interconnect thecarrier member of the second planetary gearset with the sun gear of thethird planetary gearset and the sun gear of the fourth planetarygearset; a fourth torque-transmitting mechanism selectively engageableto interconnect the ring gear of the third planetary gearset with thecarrier member of the third planetary gearset; and a fifthtorque-transmitting mechanism selectively engageable to interconnect thecarrier member of the first planetary gearset and the ring gear of thefourth planetary gearset with the ring gear of the third planetarygearset; wherein the torque transmitting mechanisms are selectivelyengageable in combinations of at least three to establish at least eightforward speed ratios and at least one reverse speed ratio between theinput member and the output member.
 11. The multiple speed transmissionof claim 10, wherein the input member is continuously interconnectedwith the carrier member of the second planetary gearset.
 12. Themultiple speed transmission of claim 10, wherein the output member iscontinuously interconnected with the carrier member of the fourthplanetary gearset.
 13. The multiple speed transmission of claim 10,wherein the plurality of interconnecting members includes a firstinterconnecting member continuously interconnecting the sun gear of thefirst planetary gearset with the sun gear of the second planetarygearset.
 14. The multiple speed transmission of claim 10, wherein theplurality of interconnecting members includes a second interconnectingmember directly connected to the ring gear of the first planetarygearset.
 15. The multiple speed transmission of claim 10, wherein theplurality of interconnecting members includes a third interconnectingmember continuously interconnecting the carrier member of the firstplanetary gearset with the ring gear of the fourth planetary gearset.16. The multiple speed transmission of claim 10, wherein the pluralityof interconnecting members includes a fourth interconnecting membercontinuously interconnecting the ring gear of the second planetarygearset with the carrier member of the third planetary gearset.
 17. Themultiple speed transmission of claim 10, wherein the plurality ofinterconnecting members includes a fifth interconnecting member directlyconnected to the ring gear of the third planetary gearset.
 18. Themultiple speed transmission of claim 10, wherein the plurality ofinterconnecting members includes a sixth interconnecting membercontinuously interconnecting the sun gear of the third planetary gearsetwith the sun gear of the fourth planetary gearset.
 19. A multiple speedtransmission, comprising: an input member; an output member; first,second, third and fourth planetary gearsets each having a sun gear, aring gear, and a carrier member; a plurality of interconnecting memberseach connected between at least one of the first, second, third, andfourth planetary gearsets and at least another of the first, second,third, and fourth planetary gearsets; a first torque-transmittingmechanism selectively engageable to interconnect the sun gear of thefirst planetary gearset and the sun gear of the second planetary gearsetwith a stationary member; a second torque-transmitting mechanismselectively engageable to interconnect the ring gear of the firstplanetary gearset with the stationary member; a thirdtorque-transmitting mechanism selectively engageable to interconnect thecarrier member of the second planetary gearset with the sun gear of thethird planetary gearset and the sun gear of the fourth planetarygearset; a fourth torque-transmitting mechanism selectively engageableto interconnect the ring gear of the third planetary gearset with thecarrier member of the third planetary gearset; a fifthtorque-transmitting mechanism selectively engageable to interconnect thecarrier member of the first planetary gearset and the ring gear of thefourth planetary gearset with the ring gear of the third planetarygearset; a first interconnecting member continuously interconnecting thesun gear of the first planetary gearset with the sun gear of the secondplanetary gearset; a second interconnecting member directly connected tothe ring gear of the first planetary gearset; a third interconnectingmember continuously interconnecting the carrier member of the firstplanetary gearset with the ring gear of the fourth planetary gearset; afourth interconnecting member continuously interconnecting the ring gearof the second planetary gearset with the carrier member of the thirdplanetary gearset; a fifth interconnecting member directly connected tothe ring gear of the third planetary gearset; and a sixthinterconnecting member continuously interconnecting the sun gear of thethird planetary gearset with the sun gear of the fourth planetarygearset; wherein the torque transmitting mechanisms are selectivelyengageable in combinations of at least three to establish at least eightforward speed ratios and at least one reverse speed ratio between theinput member and the output member.
 20. The multiple speed transmissionof claim 19, wherein the input member is continuously interconnectedwith the carrier member of the second planetary gearset, and the outputmember is continuously interconnected with the carrier member of thefourth planetary gearset.